UNIVERSITY  OF  CALIFORNIA 
AT   LOS  ANGELES 


Cotton  Mill  Machinery 
Calculations. 

A    Complete,    Comprehensive    and    Practical    Treat- 
ment of  all  Necessary   Calculations  on 

Cotton  Carding  and  Spinning  Machines. 


-BY- 


B.  M.  PARKER,  B.  s.. 

Asst.  Professor,  Carding  and  Spinning,  Textile  Dept. 
N.  G.  College  of  A.  &  M    Arts. 


PRICE    81.5O 


Published  by  B.  M.  PARKER, 

WEST  RALEIGH,  N.  G. 


WASHBURN    PRESS 

(RAY  PRINTING  co.) 

CHARLOTTE,    N      C. 


TS 


PREFACE. 

This  book  is.  intended  to  fill  what,  to  the  Author,  has  been  a 
long-felt  want,  that  is,  a  book  that  would  give  the  practical  calcula- 
tions that  are  needed  in  running  a  cotton  mill,  from  pickers  to 
looms,  in  a  simple,  straight-forward  manner,  so  as  to  be  easily 
understood  and  mastered  by  any  one  who  understands  simple 
arithmetic. 

It  is,  in  great  part,  a  reprint  of  a  series  of  articles  that  were 
written  for  and  printed  by  "Cotton"  during  the  years  1911  and 
1912,  being  entirely  revised  and  somewhat  enlarged,  with  the  addi- 
tion of  numerous  tables  scattered  throughout  its  length,  and  cov- 
ering practically  all  the  calculations,  simple  and  otherwise,  that 
any  one  would  ever  need  in  handling  a  modern  mill. 

Wherever  possible,  long  tedious  descriptions  of  individual 
mechanisms,  peculiar  to  some  one  make  or  type  of  machine,  have 
been  omitted,  as  this  was  not  the  object  in  writing  the  book,  but 
no  pains  have  been  spared  to  make  the  calculations  complete  yet 
simple  and  easily  understood. 

As  will  be  noticed,  the  tables  occurring  at  the  end  of  the  dif- 
ferent chapters  of  the  book,  are  mostly  taken  from  the  catalogues 
of  some  of  the  cotton  mill  machine  builders  and  the  Author  wishes 
here  to  express  his  appreciation  of  their  kindness  in  allowing  the 
use  of  such  tables. 

Criticisms  of  this  work,  made  in  a  spirit  of  friendliness,  will 
be  gladly  received,  as  it  is  almost  impossible  to  prevent  the  occur- 
rence of  a  few  mistakes. 

With  the  above  remarks,  the  work  is  submitted  for  the 
approval  of  the  public  and  with  the  hope  that  it  will  be  the  means 
of  bringing  a  more  thorough  understanding  of  the  calculations 
used  in  the  mill  to  some  who  have  found  them  a  little  puzzling. 

THE  AUTHOR. 
West  Raleigh,  N.  C. 
October,  1912. 


443971 


Copyrighted  February  1st,  1913 

By  B.  M.  Parker,  B.  S., 

West  Raleigh,  N.  C. 


TABLE  OF  CONTENTS. 


Page. 

CHAPTER  I — Discussion  of  Motion  —  Draft  —  Calculating 
Draft  from  Gearing — Actual  and  Figured  Drafts 
Compared — Intermediate  and  Break  Drafts 7 

CHAPTER  II — Calculations     for     Pickers  —  Draft — Speed — 

Length  of  Lap — Production  Constant 15 

CHAPTER  III — Card     Calculations — Draft — Doffer     Speed — 

Use  of  Draft,  Doffer  Speed  and  Production  Constants     32 

CHAPTER  IV — Combing     Process — Calculations    for   Draft, 
Speed  and  Production  on  Sliver  and  Ribbon  Lappers — 
Combers,  Draft,  Production  and  Waste  Calculations — 
Production  Constants    50 

CHAPTER  V — Railway  Heads  and  Drawing  Frames — Draft, 
Speed  and  Production  Calculations — Metallic  and 
Leather  Rolls — Production  Constants 69 

CHAPTER  VI — Hanks  and  Numbers 84 

CHAPTER  VII — Fly  Frames — Draft — Roll  Settings — Twist — 
Differential  or  Compound— Winding — Cones — Ten- 
sion, Lay,  Take-up  or  Bottom  Cone  and  Taper  Gear- 
ing— Production — Production  Constant  92 

CHAPTER  VIII — Spinning — Draft,  Twist,  Speed — Production 

— Roll  Setting — Average  Numbers  126 

CHAPTER  IX — Twisting — Counts  of  Ply  Yarns — Amount  of 
Twist — Twist  Calculations  and  Constant — Production 
Calculations  and  Constant  142 

CHAPTER  X — Organization — Draft  Proportioning — Program 
of  Drafts,  Weights  and  Numbers — Machinery  Equip- 
ment— Number  of  Looms . .  .  155 


CHAPTER  I. 


DISCUSSION    OF    MOTION — DRAFT — CALCULATING    DRAFT    FROM 
GEARING — ACTUAL  AND  FIGURED  DRAFTS  COMPARED — INTER- 

MEDIATE  AND  BREAK  DRAFTS. 

MOTION. 

When  two  gears  are  meshed  together,  such  as  A  and  B,  and 
motion  is  given  to  one,  A,  the  speed  of  the  other,  B,  will  depend 
upon  the  speed  of  A,  the  number  of  teeth  in  A,  and  the  number  of 
teeth  in  B.  If  A  and  B  have  the  same  number  of  teeth,  the  speed 
of  B  will  equal  the  speed  of  A.  If  A  has  twice  the  number  of 
teeth  of  B,  the  speed  of  B  will  be  twice  the  speed  of  A ;  and  if  B 
has  twice  the  number  of  teeth  of  A,  the  speed  of  B  will  be  one-half 
the  speed  of  A.  Suppose  A  to  have  40  teeth  and  B  20  teeth,  then 
the  relative  speed  of  B  as  compared  with  the  speed  of  A,  will  be 
40  -r-  20  or  2 ;  and  if  A  is  making  10  revolutions  per  minute,  the 
speed  of  B  will  be  twice  the  speed  of  A  or  20  revolutions  per  min- 
ute. If  A  had  90  teeth  and  B  30  teeth,  then  speed  of  B  would  have 
been  three  times  the  speed  of  A.  If  A  was  making  25  revolutions 
per  minute,  the  speed  of  B  would  have  been  3  x  25  =  75  revolu- 
tions per  minute.  In  other  words,  the  speed  of  B  will  always  be  to 
the  speed  of  A,  as  the  number  of  teeth  in  A  is  to  the  number  of 
teeth  in  B. 

Looking  at  this  in  another  way,  we  can  say  that  the  speed  of 
A,  multiplied  by  the  number  of  teeth  in  A,  will  always  give  a  pro- 
duct that  will  be  the  same  as  the  product  of  multiplying  the  speed 
of  B  by  the  number  of  teeth  in  3-  Putting  this  in  the  form  of  a 
rule,  we  have : 

The  speed  of  A  multiplied  by  the  number  of  teeth  in  A,  and 
this  product  divided  by  the  number  of  teeth  in  B  will  give  thet 
speed  of  B. 

This  is  always  true  and  must  be  kept  in  mind  in  dealing  with 
speed  calculations.  Taking  the  last  problem  above,  the  speed  of  B 
is  found  as  follows: 

25X90 

=  75  revolutions  per  minute,  speed  of  B. 

30 

If  gears  A  and  B  are  separated  by  one  or  more  intermediate 
gears,  as  shown  in  Fig.  1  the  same  statements  hold  good,  as  the 
intermediate  gears  C  and  D  simply  serve  to  transmit  the  motion 
of  A  to  B,  and  will  in  no  wise  affect  the  speed  of  B  regardless  of 


8  COTTON   MILL  MACHINERY   CALCULATIONS. 

the  number  of  teeth  in  either  one  of  the  intermediates.  Such  gears 
are  used  simply  to  fill  in  the  space  between  A  and  B  or  to  change 
the  direction  of  motion  of  B,  and  are  called  "idler"  or  "carrier" 
gears.  When  a  gear  receives  motion  at  its  axis  or  center,  by  vir- 
tue of  being  atached  to  a  revolving  shaft,  and  conveys  this  motion, 
through  its  outer  edge  or  rim,  to  another  gear,  it  is  a  driving  gear 
or  driver ;  and  any  alteration  in  its  speed  or  the  number  of  teeth 
will  directly  affect  the  speed  of  all  the  gears  controlled  by  it  in  the 
same  proportion.  In  Fig.  1  A  is  a  driving  gear,  and  doubling  its 
speed  or  number  of  teeth  will  double  the  speed  of  B. 

When  a  gear  receives  motion  at  its  outer  edge  or  rim  and  con- 
veys it  thence  to  its  axis,  before  aifecting  any  other  gear,  it  is  a 
driven  gear.  In  Fig.  1  B  is  a  driven  gear,  and  any  change  in  the 
number  of  teeth  of  B  will  affect  its  speed  in  inverse  ratio ;  as 
doubling  the  number  of  teeth  of  B  will  divide  its  speed  by  two,  and 
consequently  the  speed  of  any  gears  controlled  by  the  shaft  on 
which  B  is  located  will  be  affected  the  same  way. 

When  a  gear  receives  motion  on  its  outer  rim  and  conveys  it 
along  its  rim  to  another  gear,  it  is  an  idler  gear  or  "carrier."  Any 
change  in  the  number  of  teeth  of  such  gear  has  no  effect  on  the 
speed  of  any  of  the  succeeding  gears  in  the  train.  A  gear  may  act 


FIG.  1.    DIAGRAM  ILLUSTRATING  A  SIMPLE  TRAIN  OF  GEARS 
IN  MESH. 


as  a  carrier  in  relation  to  one  train  of  gearing  and  also  as  a  driver 
or  driven  gear  in  relation  to  another  train  of  gearing. 

In  the  form  of  gearing  shown  in  diagram  Fig.  2  we  have  a 
different  arrangement.  A  and  B  are  connected  by  means  of  two 
gears  C  and  D  and  a  shaft  E,  the  two  gears  C  and  D  being  fixed 
on  the  shaft  E,  which  means  that  they  will  have  the  same  speed 
regardless  of  the  number  of  teeth  they  may  have.  The  gears  C 
and  D  are  not  carrier  gears,  as  D  receives  motion  at  its  rim  from 
A  and  passes  the  motion  to  the  shaft  at  its  center,  while  C  receives 
motion  at  its  center  from  the  shaft  and  transmits  it  to  B  at  its  rim. 


INTRODUCTION. 


FIG.  2.    DIAGRAM  ILLUSTRATING  A  COMPOUND  TRAIN  OF  GEARING 
IN  MESH. 

Suppose  A  to  have  40  revolutions  per  minute ;  then  the  speed  of  D 
will  be : 

40X90 

—  =  120  revolutions  per  minute. 
30 

As  the  speed  of  D  is  *120,  the  speed  of  C  will  also  be  120,  and 
we  can  take  this  speed  and  follow  the  same  rule  and  find  the  speed 
of  B  as  follows : 

120X50 

— =  150  revolutions  per  minute. 

40 

Finding  the  speed  of  B  in  one  operation  is  a  matter  of  sim- 
ply combining  the  two  formulas  as  follows : 

40X90       50 

— •  X  —  =  150  revolutions  per  minute. 
40  40 

In  the  above  it  will  be  seen  that  gears  A  and  C  are  drivers, 
and  D  and  B  are  driven  gears. 

PULLEY  CALCULATIONS. 

In  dealing  with  pulleys  the  same  statements  and  rules  as  for 
gears  hold  good,  using  the  pulley  diameters  instead  of  the  number 
of  teeth. 

Rule  for  pulleys : 

Multiply  together  the  speed  of  the  driving  pulley  and  its 
diameter,  and  divide  by  the  diameter  of  the  driven  pulley.  The 
quotient  will  be  the  speed  of  the  driven  pulley. 

There  are  several  ways  of  stating  the  above  rule,  but  the  one 
given  is  very  simple.  The  main  point  to  remember  is  that  the  pro- 
duct of  the  diameter  and  speed  of  the  driving  pulley  in  all  cases 


10  COTTON  MILL  MACHINERY   CALCULATIONS. 

will  be  the  same  as  the  product  of  the  speed  and  diameter  of  the 
driven  pulley. 

Example :  Suppose  the  driving  shaft  in  a  mill  to  be  running 
300  revolutions  per  minute  and  has  a  10  inch  pulley  on  it  driving  a 
machine  that  has  a  20  inch  pulley  on  it.  The  revolutions  per  min- 
ute of  the  20  inch  pulley  would  be : 

300X10 

=  150  revolutions  per  minute. 

20 

Suppose  you  knew  the  required  speed  of  the  shaft  of  the  ma- 
chine, the  size  of  its  pulley,  and  the  speed  of  the  driving  shaft, 
and  wanted  to  find  the  size  of  the  pulley  to  put  on  the  driving  shaft. 
The  products  of  the  speeds  and  diameters  must  be  equal,  so  that 
the  product  of  the  speed  and  diameter  of  the  known  pulley,  divided 
by  the  speed  of  the  required  pulley,  will  give  the  diameter  of  the 
required  pulley. 

150X20 

=  10  inches. 

300 

So  far  we  have  dealt  only  with  speeds  of  rotation  expressed  in 
revolutions  per  minute.  In  many  calculations  we  use  the  surface 
or  circumferential  speeds  of  pulleys  and  different  parts  of  ma- 
chines. The  circumference  of  any  pulley  or  roll  is  equal  to  its 
diameter  multiplied  by  3.1416.  The  surface  or  circumferential 
speed  of  any  pulley  or  roll  is  equal  to  its  circumference  multiplied 
by  its  revolutions  per  minute.  In  the  preceding  example,  the  pul- 
ley on  the  shaft  would  have  a  surface  speed  of: 

300  x  10  x  3.1416  =  9,425  inches  or  785.4  per  minute.  The 
pulley  on  the  shaft  of  the  machine  must  take  up  as  much  belt  as  is 
delivered  by  the  pulley  on  the  driving  shaft,  that  is,  its  surface 
speed  must  be  equal  to  the  surface  speed  of  the  driving  pulley,  or 
785.4  feet. 

The  preceding  explanation  should  enable  any  one  to  under- 
stand all  the  calculations  relating  to  speeds  as  they  may  come  up 
later  on. 

DRAFT. 

Every  machine  that  operates  on  the  cotton,  from  the  time  it 
is  opened  in  the  picker  room  until  it  is  spun  on  bobbins  in  the  spin- 
ning room  in  the  shape  of  yarn,  has  a  certain  amount  of  draft.  It 
will  be  well  to  find  out  exactly  what  draft  is  before  we  attempt 
to  figure  drafts  on  the  machine.  The  object  of  draft  in  cotton  mill 
machinery  is  to  secure  a  gradual  reduction  of  the  mass  of  cotton 
as  it  is  fed  into  the  pickers  to  the  size  of  the  spun  thread  as  it  leaves 
the  rolls  of  the  spinning  frame.  Every  machine  has  its  part  to 


INTRODUCTION.  11 

perform  in  reducing  the  bulk  or  weight.  Draft,  then,  is  a  reduc- 
tion in  bulk  or  weight  and  a  consequent  increase  in  the  length  of 
the  material  under  operation  and  is  therefore  the  relative  surface 
speed  of  the  feed  roll  and  delivery  roll  of  the  machine. 

To  illustrate :  Suppose  a  machine  receives  cotton  at  the  rate 
of  10  yards  a  minute  and  delivers  it  at  the  rate  of  60  yards  a  min- 
ute, or  six  times  the  length  it  receives,  the  draft  of  the  machine 
will  be  six,  that  is,  for  every  yard  received  it  would  deliver  six 
yards.  It  must  be  remembered,  however,  that  as  the  length  of  the 
material  increases,  its  weight  per  yard  decreases;  hence  one  yard 
at  the  front  of  the  machine  will  weigh  only  one-sixth  of  the  amount 
of  the  same  length  at  the  back  of  the  machine.  If  the  material 
entering  the  above  machine  weighed  60  grains  per  yard  the  total 
weight  fed  in  per  minute  would  be  600  grains.  The  machine  must 
turn  out  the  same  weight  in  the  same  time  as  is  fed  into  it,  so  there 
will  have  to  be  600  grains  fed  out  per  minute,  but  this  weight  must 
be  spread  over  the  60  yards  instead  of  10  yards  and  each  yard  will 
weigh  only  10  grains  or  one-sixth  of  what  it  did  when  fed  into  the 
machine. 

From  the  above  it  will  be  seen  that  the  draft  can  be  express- 
ed in  two  ways : 

(1)  Draft  is  the  ratio  between  the  weight  per  yard  fed  into 
and  delivered  by  the  machine,  and  can  be  found  by  dividing  the  to- 
tal weight  per  yard  entering  the  machine  by  the  weight  per  yard 
delivered  by  the  machine. 

(2)  Draft  is  the  ratio  of  the  surface  speeds  of  the  receiving 
and  delivery  rolls,  and  can  be  obtained  by  dividing  the  length  de- 
livered by  the  machine  by  the  length  fed  into  it  in  a  given  time. 

The  drafts  of  the  different  machines  depend  upon  the  arrange- 
ment of  the  machinery  and  the  layout  of  the  mill.  They  may  be 
varied  in  the  machines  within  certain  limits.  Usually  the  smaller 
the  mass  of  cotton  being  handled,  the  greater  the  draft. 

CALCULATING  DRAFT  FROM  THE  GEARING. 

There  are  different  rules  for  finding  draft.  The  method  il- 
lustrated below  will  prove  easy  of  application,  suits  the  most  com- 
plicated gearing  found,  needs  no  considering  of  driving  and  driven 
gears  and,  from  actual  experience,  is  found  to  be  most  easily  un- 
derstood and  worked  . 

Draw  a  straight  horizontal  line,  put  the  diameter  of  the  front 
roll  above  the  line,  the  number  of  teeth  in  the  gear  on  the  front  roll 
under  the  line,  the  next  gear  meshing  into  it  above  the  line,  the 
next  under.  Continue  this  until  the  diameter  of  the  back  roll  is 
reached  which  naturally  comes  under  the  line.  Leave  out  all  car- 


12 


COTTON  MILL  MACHINERY   CALCULATIONS. 


rier  gears  in  thus  preparing  for  the  calculation..  Multiply  together 
the  figures  above  the  line  and  divide  this  product  by  the  product 
of  all  the  figures  under  the  line.  The  answer  will  be  the  draft  of 
the  machine. 

The  points  to  be  noted  are :  Always  start  the  calculation  with 
the  front  roll  diameter  over  the  line  and  finish  with  the  back  roll 
diameter  under  the  line.  If  all  idler  gears  are  left  out  of  the  cal- 
culation there  will  be  the  same  number  of  figures  above  as  below 
the  line. 

Fig.  3  represents  three  drawing  rolls  connected  by  gearing 
and  illustrates  the  arrangement  found  on  fly  frames.  Applying  the 
rule  just  given  we  get  the  following: 


1%X100X56 
37X34X1 


=  5  draft  between  front  and  back  rolls. 


In  all  cases  it  will  simplify  matters  to  express  the  diameters 
of  the  two  rolls  in  the  same  terms.  In  the  above  the  11%-inch 
front  roll  can  be  expressed  as  9,  and  the  back  roll  as  8. 

In  every  train  of  draft  gearing  a  "change"  gear  is  located  at 
some  convenient  point.  By  changing  the  size  of  the  gear,  the  ratio 
between  the  surface  speeds  of  the  delivery  and  feed  rolls  is  chang- 
ed, thus  changing  the  draft.  This  gear  is  spoken  <xf  as  the  draft 
.hange  gear  or  draft  gear.  It  is  not  necessary  to  work  through 
the  entire  train  of  gearing  every  time  a  change  in  draft  is  desired 


E 


X       F*  0  t-  L         / 


=0=Jl 

fr      »ot-L.      f~. 


FIG.  3.    DIAGRAM  OF  A  TISAIN  OF  GEARS  FOR  DRAFTING  EOLLS. 

and  the  usual  custom  is  to  work  out  a  draft  factor  or  "constant" 
for  the  machine  which,  divided  by  the  draft  gear,  will  give  the 
draft,  or  divided  by  the  draft  will  give  the  draft  gear.  In  Fig.  3 


INTRODUCTION.  13 

the  34  tooth  gear  is  the  draft  gear.  By  leaving  this  gear  out  of  the 
calculation  for  draft  just  given,  but  retaining  all  the  other  figures 
in  the  same  relative  positions,  we  get  the  draft  constant,  as  fol- 
lows: 

9  X100X56 
=  170.27  draft  constant. 


37XXX  8 

To  find  the  draft : 

170.27  -*-  34  =  5  draft. 

To  find  the  draft  gear : 

170.27  -s-  5  =  34  draft  gear. 

From  the  above  we  get  the  following  rules  in  regard  to  draft 
that  apply  to  practically  every  machine  in  use  in  the  mill : 
Constant  -=-  draft  =  gear. 
Constant  -j-  gear  =  draft. 
Draft  x  gear  =  constant. 

INTERMEDIATE  DRAFTS. 

In  the  foregoing  only  the  draft  between  the  front  and  back 
rolls  or  the  total  draft  has  been  considered.  The  total  draft  on 
every  machine  is  split  into  two  or  more  intermediate  drafts- 
Referring  to  Fig.  3  there  will  be  noticed  two  different  drafts, 
namely,  the  draft  occurring  between  the  front  and  middle  rolls  and 
the  draft  occurring  between  the  middle  and  back  rolls.  The  draft 
between  any  two  such  intermediate  points  can  be  found  by  apply- 
ing the  foregoing  rule,  always  considering  the  two  points  under 
discussion  as  the  receiving  and  delivering  rolls,  regardless  of  their 
relative  positions  to  the  other  rolls  in  the  machine. 

Figuring  the  draft  between  the  front  and  middle  rolls  in  Fig. 
8,  we  get : 

9X100X56X20 

=  4.77  draft. 

37X34X21X8 

The  draft  between  the  middle  and  back  rolls  is  found  by  same 
method. 

1  X21 

1.05  draft. 


20X  1 

In  this  case  we  must  consider  the  middle  roll  as  the  delivery 
roll  of  the  two.  The  product  of  all  the  intermediate  drafts  of  any 
machine  is  equal  to  the  total  draft.  Taking  the  two  intermediate 
drafts  above  we  find  their  product  is  5,  which  is  the  same  as  the 
total  draft  previously  figured. 


14  COTTON  MILL   MACHINERY   CALCULATIONS. 

BREAK  DRAFT. 

In  changing  the  total  draft  of  a  machine  by  making  a  change 
in  the  size  of  the  draft  gear,  we  alter  only  one  of  the  intermediate 
drafts,  the  other  drafts  in  the  machine  remaining  the  same.  In 
fhe  above  case  any  change  in  the  draft  gear  will  affect  the  total 
draft  between  the  front  and  back  rolls,  but  wiK  not  affect  the  draft 
between  the  middle  and  back  rolls.  To  change  the  draft  between 
these  would  require  a  change  in  the  size  of  either  the  20  or  21  tooth 
£ears.  This  intermediate  draft  is  spoken  as  the  br<«ak  draft  to  dis- 
tinguish it  from  the  other  intermediate  drafts. 

TENSION  DRAFT. 

There 'is  only  a  very  slight  draft  occurring  between  certain 
points  on  machines  in  a  mill  which  serves  the  purpose  of  keeping 
the  material  tight  so  there  will  be  no  undue  sagging  of  the  ends. 
These  drafts  are  not  enough  to  materially  affect  the  total  draft  of 
the  machine  or  the  weight  of  the  finished  product.  They  are 
sometimes  spoken  of  as  tension  drafts  or  more  commonly  refer- 
red to  simply  as  tension. 


PICKERS. 

CHAPTER  II. 


15 


CALCULATIONS  FOR  PICKERS — DRAFT — SPEED — LENGTH  OF  LAP — 
PRODUCTION — PRODUCTION  CONSTANTS. 

DRAFT  OF  PICKERS.     « 

The  draft  of  the  breaker  picker  is  small  and  seldom  changed, 
any  desired  change  in  the  weight  of  the  breaker  laps  being  usually 
secured  by  changing  the  amount  of  feed  on  the  automatic  feeder. 
The  draft  ranges  between  1.5  and  2.  The  draft  of  the  intermedi- 


FIG.  4.    DIAGRAM  OF  GEARING  ON  THE  KITSON  BREAKER  PICKER. 

ate  and  finisher  pickers  is  about  4,  with  4  laps  fed  in  at  the  back 
and  the  evener  belt  driving  at  the  middle  of  the  cones. 

Fig.  4  shows  the  gearing  of  the  Kitson  breaker  picker.  There 


16  COTTON   MILL  MACHINERY   CALCULATIONS. 

is  no  draft  change  gear  on  this  machine. 

To  calculate  the  draft  of  the  breaker  picker  from  the  gearing 
shown  in  Fig.  4,  start  with  the  9  inch  lap  roll,  placing  it  above  the 
line,  and  alternate  the  gears  below  and  above  the  line  until  the 
feed  roll  is  reached,  the  latter  coming  under  the  line,  as  in  figures 
used  in  the  previous  chapter: 

9  X18X14X36X15X26X38 

=  1.85  draft 

37X73X13X26X15X19X2.5 

Fig.  5  shows  the  gearing  plan  of  a  Kitson  intermediate 
picker  or  lapper  with  a  two-bladed  beater  to  revolve  at  1500  R.  P. 
M.  The  gearing  for  the  finisher  picker  is  the  same  as  for  the  in- 
termediate. To  calculate  the  draft  of  the  intermediate  picker 
from  the  gearing  shown  in  Fig  5,  using  a  23  tooth  draft  gear, 
start  with  the  9  inch  lap  roll,  placing  it  above  the  line  and  pro- 
ceeding as  in  the  calculation  on  the  breaker  picker : 

9X18X14X14X30X54X3.25X85X28X12 

=  3.95  draft. 

37X73X76X23X40X10X1X20X16X2 

To  work  out  a  draft  constant,  use  the  same  figures  as  above, 
but  leaving  out  the  23  tooth  draft  gear  and  substituting  X  in  its 
place,  as  follows : 

9X18X14X14X30X54X3.25X85X28X12 

=  90.86. 

37X73  X76XXX40X10X1X20X16X2 

As  the  draft  gear  comes  under  the  line,  the  draft  constant 
90.86,  must  be  divided  by  the  draft  gear  to  obtain  the  draft. 

90.86 -r- 23  =  3.95  draft. 

Now  to  find  the  correct  gear  to  give  any  desired  draft,  divide 
the  draft  constant  by  the  draft  desired. 

90.86^-3.95  =  23.1  or  23  tooth  draft  gear. 

In  all  calculations  in  which  the  answer  is  the  number  of  teeth 
in  a  gear,  use  a  whole  number  as  the  final  answer.  A  good  rule 
to  follow  is  to  work  out  the  answer  to  the  first  decimal  and,  if  this 
fraction  is  less  than  .5,  discard  it,  as  in  the  above  case,  but  in- 
crease the  whole  number 'by  one  in  case  the  fraction  is  .5  or  over. 
If  the  answer  of  the  above  calculation  had  been  23.5,  we  would 
have  given  it  as  24  teeth.  For  all  practical  purposes  91  can  be 
used,  as  the  draft  constant  instead  of  90.86,  as  the  small  amount 
of  increase  necessary  to  bring  it  to  a  whole  number  will  not  affect 
the  results  to  any  appreciable  extent. 

It  will  be  noticed  from  Fig.  5,  that  any  change  in  the  size  of 
the  draft  gear  will  affect  the  speed  of  the  feed  rolls  only  and  will 


PICKERS. 


17 


not  alter  the  speed  of  the  cages,  lap  or  calendar  rolls.  A  larger 
draft  gear  will  drive  the  feed  rolls  faster  and  cause  them  to  feed 
in  more  cotton,  and  thus  lessen  the  draft.  The  largest  portion  of 
the  draft  on  the  pickers  occurs  between  the  feed  rolls  and  the 
screens  or  cages,  and  any  change  in  the  total  draft  occurs  be- 
tween these  two  points.  The  drafts  between  the  other  intermedi- 
ate points,  such  as  cages  to  stripping  rolls,  stripping  rolls  to  calen- 


73 


^IG.  5.    DIAGRAM  OF  GEARING  ON  THE  KITSON  FINISHER  PICKER. 


der  rolls  and  calender  rolls  to  lap  rolls,  are  very  small.  These 
drafts  are  spoken  of  as  tension  and  only  serve  the  purpose  of 
keeping  the  material  tight  as  it  is  passed  through  the  machine. 
Considering  the  cages  as  the  delivery  rolls  and  working  back  to 


18  COTTON   MILL  MACHINERY   CALCULATIONS. 

the  feed  rolls,  using  the  same  method  as  before,  we  get  the  follow- 
ing: 

22X68X14X13X14X30X54X3.25X85X28X12 

=  3.07    draft    between    the 

180X29X80X76X23X40X10X1X20X16X2         [cages  and  the  feed  rolls. 

Not  considering  the  tension  draft  between  the  different 
points,  we  can  get  the  draft  between  the  cages  and  the  lap  rolls 
by  the  following  calculation: 

9   X18X14X80X29X180 

—  =  1.29  draft. 
37X73X13X14X68X22 

The  product  of  these  two  intermediate  drafts  will  be  the  total 
draft,  thus: 

3.07  X  1.29  =  3.96  total  draft. 

By  similar  figuring,  it  is  possible  to  work  out  all  the  interme- 
diate drafts  or  find  the  draft  between  any  two  points  on  the  ma- 
chine. In  the  above  figuring,  the  cone  or  evener  belt  is  considered 
to  be  working  in  the  middle  of  the  cones,  as  this  is  considered  best 
by  most  carders.  The  diameter  of  the  driven  cone  at  this  point  is 
3.25  inches.  The  numeral  1  in  the  calculation  is  the  single  worm 
on  the  end  of  the  driving  cone.  Some  carders  prefer  to  run  the 
cone  belt  about  one-third  the  distance  from  the  large  end  of  the 
driven  cone.  In  this  case  the  diameter  of  the  cone  can  be  taken 
as  4.  This  would  give  a  draft  constant  of  112,  and  a  23  tooth 
draft  gear  would  give  a  draft  of  4.87  instead  of  3.95. 

It  is  seldom  necessary  to  change  the  draft  gear  on  the  pick- 
ers, because  the  cone  drive  to  the  feed  rolls  permits  of  such  wide 
variations  in  draft  by  simply  moving  the  evener  belt.  The  range 
of  drafts  used  also  is  small  and  any  radical  change  desired  in  the 
weight  of  finished  laps  is  usually  made  in  the  feed  of  the  machine. 

In  figuring  the  draft  from  the  weight  of  cotton  being  fed 
into  and  delivered  by  the  machine,  the  rule  is: 

Divide  the  weight  going  in  at  the  back  by  the  weight  coming 
out  at  the  front. 

i  Example:  There  are  four  laps  on  the  apron  of  the  picker, 
each  weighing  14  ounces  per  yard.  The  lap  delivered  weighs  14.5 
ounces  per  yard.  What  is  the  draft? 

4X14 

—  =  3.76  draft. 
14.5 

Draft  thus  figured  from  the  actual  weight  on  the  front  and 
back  of  a  machine,  is  spoken  of  as  actual  draft  and,  on  every  ma- 
chine that  produces  waste,  the  actual  draft  is  larger  than  the  fig- 
ured draft  obtained  from  the  gearing.  In  other  words  the  actual 


PICKERS.  19 

draft  is  the  ratio  between  the  weight  fed  into  the  machine  and 
the  weight  delivered  from  the  machine.  It  takes  into  account 
any  loss  of  cotton  in  the  form  of  waste  that  may  occur  between 
the  feed  and  delivery  rolls.  Figured  draft  is  the  ratio  between 
the  surface  speeds  of  the  delivery  roll  and  feed  roll,  and  remains 
the  same  regardless  of  the  amount  of  cotton  lost  In  the  form  of 
waste. 

On  the  pickers  we  can  count  on  losing  about  3  per  cent,  or 
more  as  waste  of  the  total  amount  of  cotton  fed  into  the  machine, 
depending  upon  the  grade  of  cotton  being  handled  and  the  cleanli- 
ness desired  in  the  finished  product.  Now  if  the  picker  takes  out 
3  per  cent,  waste,  the  amount  delivered  from  the  machine  will  rep- 
resent 97  per  cent,  of  the  amount  fed  into  the  machine.  Then  the 
amount  going  in  at  the  back  must  be  decreased  by  the  amount  of 
waste  made  before  we  can  figure  the  actual  weight  at  the  front. 

To  illustrate  this  point :  If  we  figure  the  draft  of  the  picker 
from  the  gearing  to  be  3.95,  and  there  are  4  laps  on  the  apron 
each  weighing  16  ounces  per  yard,  then  the  following  should  give 
the  theoretical  weight  of  lap  at  the  front. 

4X16 

—  =  16.2  ounces  per  yard. 
3.95 

Now  to  allow  for  the  loss  in  weight,  on  account  of  the  3  per 
cent,  waste  taken  out,  we  must  multiply  the  weight  at  the  back 
by  .97,  and  then  find  what  the  weight  on  the  front  will  be : 

16X4X.97 

=  15.71  ounces  per  yard. 

3.95 

The  actual  draft  of  the  machine  figured  from  the  weight  on 
the  front  and  the  back  would  be  this : 

16X4 


4.07  draft. 


15.71 

It  will  be  seen  from  the  above  that  using  a  23  tooth  gear  which 
we  have  figured  to  give  us  a  draft  of  3.95  with  16  ounce  laps  on 
back  and  a  loss  of  3  per  cent,  waste,  we  would  actually  have  a 
draft  of  4.07  and  the  lap  would  weigh  15.71  ounces  per  yard  in- 
stead of  16.2  ounces  per  yard.  In  actual  practice  this  would  not 
make  any  difference,  as  the  correct  weight  of  laps  would  be  ob- 
tained by  a  slight  change  in  position  of  the  evener  belt. 

In  the  same  way  in  finding  the  weight  of  laps  on  the  apron 
>f  the  picker  from  the  weight  at  the  front  and  the  figured  draft, 
we  must  allow  for  the  loss  of  waste  in  order  to  be  absolutely 
accurate. 


20  COTTON  MILL  MACHINERY   CALCULATIONS. 

Example :  The  weight  of  the  lap  at  the  front  is  15.71  ounces 
per  yard,  the  waste  is  3  per  cent.,  and  the  figured  draft  is  3.95. 
What  is  the  weight  of  the  lap  at  the  back  of  the  picker? 

15.71X3.95 

—  =  16  ounces,  weight  of  lap  on  apron. 
4X57 

The  principles  underlying  these  two  problems  can  be    ex- 
pressed in  the  following  formulas,  understanding  that  the  draft 
used  is  the  figured  draft  and  not  the  actual  draft: 
To  find  the  weight  of  the  lap  at  the  front : 
Wt.  at  back  x  doublings  x  1  less  per  cent,  of  waste 

draft 

To  find  the  weight  at  the  back : 
Wt.  at  front  x  draft 


doublings  x  1  less  per  cent,  of  waste 

The  expression,  1  less  per  cent,  of  waste,  is  easily  explained 
if  we  remember  that  the  percentage  of  waste  can  be  expressed 
decimally  as  well  as  the  way  given,  as  3  per  cent,  can  be  expressed 
as  .03  and  will  have  the  same  value.  Now  the.97  used  in  working 
the  two  problems  equals  1  minus  .03  equals  .97.  If  the  machine 
makes  4  per  cent,  waste,  we  would  use  .96  in  the  formula. 

SPEED. 

The  two-bladed  beater  usually  revolves  at  1,500  R.  P.  M.  while 
the  three-bladed  beater  is  run  at  about  1,200  R.  P.  M.  If  the 
Kirschner  carding  beater  is  used,  it  should  revolve  at  about  1,500 
R.  P.  M.  The  fan  runs  from  900  to  1,050  R.  P.  M.,  depending 
upon  the  amount  of  waste  desired.  The  speed  of  the  lap  rolls 
varies  from  4.5  to  9  R.  P.  M.  In  getting  the  speed  of  any  re- 
volving part  of  the  picker,  it  is  well  to  bear  in  mind  that  the 
product  of  the  driving  pulley  multiplied  by  its  diameter,  in  every 
case,  will  be  equal  to  the  product  of  the  driven  pulley  multiplied 
by  its  diameter. 

To  find  the  speed  of  the  beater  shown  in  Fig.  5  when  the  main 
shaft  speed  is  325  R.  P.  M. :  The  pulley  on  the  main  shaft  driving 
the  picker  being  28  inches  in  diameter,  the  pulley  on  the  picker 
counter  shaft  being  18  inches  in  diameter,  the  large  pulley  on 
the  counter  which  drives  the  beater  being  24  inches,  and  the  pulley 
on  the  beater  shaft  8  inches  in  diameter. 

Starting  with  the  speed  of  the  main  shaft,  we  get  the 
following : 


PICKERS.  21 

325X28X24 


18X8 


=  1,516  R.  P.  M.  of  beater. 


This  can  be  considered  as  1,500,  as  the  slippage  in  the  belts  is 
liable  to  bring  it  down  to  that  figure. 

The  speed  of  the  fan  can  be  obtained  as  follows:  The  fan 
pulley  is  8  inches  in  diameter  and  the  pulley  on  the  beater  shaft 
driving  the  fan  is  five  inches  in  diameter. 

1,500X5 

—  =  937.5  R.  P.  M.  of  fan. 
8 

In  figuring  the  speed  of  the  lap  rolls,  we  must  start  with  the 
4^>  inch  pulley  on  the  end  of  the  beater  shaft.  This  is  called  the 
ipeed  pulley,  and  the  size  of  this  pulley  controls  the  production  of 
the  picker.  Changing  the  size  of  this  pulley  changes  the  speed  of 
every  part  of  the  machine,  except  the  beater  and  fan.  A  larger 
pulley  drives  the  machine  faster,  thus  increasing  the  production. 

The  following  calculation  will  give  the  speed  of  the  lap  rolls : 

1500X4.5X14X14X18 

=  4.83  R.  P.  M. 

24X76X73X37 

In  the  above,  the  diameter  of  the  pulley  and  the 
teeth  in  the  gears  are  used  together  in  the  same  calculation,  as,  in 
either  case,  they  are  used  to  express  the  relation  between  the 
different  parts  being  considered,  and  it  makes  no  difference 
whether  this  relation  is  expressed  in  diameters  or  teeth. 

LENGTH  OP  LAP. 

The  total  weight  of  the  finished  lap  is  governed  by  the  number 
of  yards  it  contains.  It  is  measured  by  the  revolutions  of  the  lap 
rolls,  the  picker  automatically  stopping  after  the  required  number 
of  yards  are  wound.  The  regulating  device  is  called  the  knock- 
off,  a  plan  of  the  gearing  of  same  being  shown  in  Fig.  6.  The 
knock-off  or  lap  gear  makes  1  revolution  for  each  lap  wound. 
Thus  any  change  made  in  the  size  of  the  knock-off  gear  will  give 
a  corresponding  change  in  the  number  of  yards  in  the  lap ;  a 
larger  gear  will  give  more  yards  in  the  lap,  a  smaller  gear  less. 

The  lap  rolls  are  9  inches  in  diameter  or  28.27  inches  in 
circumference  and  will  have  to  make  1.27  revolutions  to  wind  up 
one  yard  of  lap.  Now  if  we  start  with  the  one  revolution  of  the 
knock-off  gear,  while  the  lap  is  forming,  and  figure  around  to  the 
9  inch  lap  roll  (see  Fig.  6) ,  we  would  get  the  number  of  revolu- 
tions of  the  lap  roll  while  the  lap  is  forming.  Then,  as  the  lap  roll 
has  to  make  1.27  revolutions  to  wind  one  yard,  if  we  divide  this  by 
1.27  we  would  get  the  number  of  yards  in  the  lap,  as  follows :  * 


COTTON  MILL  MACHINERY   CALCULATIONS. 


FIG.  6.    DIAGRAM  OF  KNOCK-OFF  GEARING. 


1X60X35X80X14X18 


52.74  yards  in  lap. 


18X1X13X73X37X1.27 

We  can  get  the  knock-off  constant  by  the  same  method  as 
above,  by  simply  leaving  out  the  knock-off  gear,  thus : 

1XXX35X80X14X18 

=  .879  constant. 

18X1X13X73X37X1.27 

The  change  gear  appears  above  the  line  in  this  case,  and  the 
constant  must  be  multiplied  by  the  gear  to  get  the  number  of  yards 
per  lap,  thus : 

.879  X  60  =  52.74  yards  in  lap. 

To  find  the  number  of  teeth  in  the  knock-off  gear  to  give  any 
desired  number  of  yards  in  the  lap : 

Divide  the  number  of  yards  in  the  lap  by  the  knock-off 
constant. 

52.74  •*•  .879  =  60  teeth  in  knock-off  gear. 
PRODUCTION. 

An  intermediate  or  finisher  picker  will  produce  from  1,500 
to  2,500  pounds  of  laps  per  day  of  10  hours,  while  the  breaker 
picker  will  produce  from  2,500  to  4,000  pounds  of  laps  a  day. 
Where  good  clean  laps  are  desired  for  the  cards  the  lower  pro- 
ductions are  recommended.  The  production  of  a  picker  depends 
upon  the  speed  of  the  lap  rolls,  the  weight  per  yard  of  the  lap 
and  the  time  lost  in  taking  off  the  full  laps,  cleaning  up,  etc. 

Suppose  the  picker  is  delivering  a  14  ounce  lap,  and  the  lap 
rolls  are  making  6  R.  P.  M.  Allowing  20  per  cent  loss  of  time, 
what  would  be  the  production  in  a  10  hour  day? 


PICKERS.  23 

The  lap  roll  is  9  inches  in  diameter  and  its  circumference  i? 
S  X  3.1416  =  28.27  inches.  It  makes  6  R.  P.  M.,  so  every  minute  it 
will  deliver  6  X  28.27  =  169.62  inches  of  lap  or  10,177.2  inches  an 
hour.  In  a  10  hour  day  it  will  deliver  10,177.2  x  10  =  101,772 
inches,  or  2,827  yards  of  lap.  Each  yard  weighs  14  ounces,  so  in 
a  day  there  will  be  2,827  x  14  =  35,578  ounces  of  lap  delivered. 
From  this  we  must  take  the  20  per  cent,  loss  of  time,  therefore 
35,578  x  .80  =  31,662.4  ounces  actually  produced.  Then  31,662.4 
-f- 16  =  1,987.9  pounds  produced  per  day.  This  calculation  has 
been  given  in  detail,  so  that  all  steps  necessary  will  be  clearly  seen 
and  understood. 

All  production  calculations  are  based  on  the  same  principles 
and  differ  only  in  tne  terms  used.  The  above  allowance  of  20  per 
cent,  loss  of  time  is  ample  for  all  necessary  stoppages  and  may  be 
considered  too  high  by  some,  but  it  is  far  better  to  make  an  error 
on  the  side  of  too  little  production  in  our  calculations  than  too 
much. 

The  above  production  problem  can  be  expressed  in  one 
formula  showing:  at  a  glance  every  step  taken  to  get  the  answer, 
thus: 

9X3.1416X6X60X10X.80X14 

—  =  1978.9  pounds. 
36X16 

In  the  above  problem  we  can  consider  everything  as  fixed 
except  the  speed  of  the  lap  rolls  and  the  weight  of  the  lap.  The 
speed  of  the  lap  rolls  varies  with  the  size  of  the  speed  pulley  to 
give  different  productions.  The  weight  of  the  lap  may  vary  from 
10  to  16  ounces  per  yard,  so,  if  we  leave  these  two  variable  quan- 
tities out  of  the  production  calculation,  and  use  the  remaining 
figures  in  the  formula,  we  get  a  production  factor  or  constant : 

9X3.1416XXX60X10X.80XX 

—  =  23.56  production  constant. 
36X16 

Rule  for  using  production  constant : 

Multiply  the  constant  by  the  weight  per  yard  of  lap  in  ounces 
and  by  the  R.  P.  M.  of  the  lap  rolls. 

The  above  constant  is  based  on  a  10  hour  day  with  an  allow- 
ance of  20  per  cent,  loss  of  time.  Using  constants  of  this  charac- 
ter on  the  different  machines  'in  the  mill  will  greatly  simplify  the 
work  necessary  in  figuring  the  production.  A  small  speed  in- 
dicator is  a  great  convenience  in  finding  the  actual  speeds  of  the 
dfferent  machines  in  the  mill  under  working  conditions.  With 
it  the  speed  of  any  machine  or  revolving  part  of  the  machine 
can  be  found. 


24  COTTON  MILL  MACHINERY   CALCULATIONS. 

There  are  other  methods  in  use  for  figuring  production  on 
pickers  with  the  same  idea  in  view  of  simplifying  the  work.  The 
two  following  rules  are  taken  from  the  Kitson  catalogue  and  will 
give  correct  answers. 

Rule  to  find  the  production  of  a  picker  for  a  day  of  10  hours, 
allowing  10  per  cent,  loss  of  time: 

Multiply  the  weight  of  lap  in  ounces  per  yard  by  the  R.  P.  M. 
of  beater  and  by  the  diameter  of  the  feed  pulley  and  divide  this 
product  by  52. 

Example:  The  weight  of  lap  is  13  ounces  per  yard;  beater 
speed  is  1,500  R.  P.  M. ;  and  the  feed  pulley  is  6  inches  in  diameter. 
What  is  the  production? 

13X1,500X6 

—  =  2,250  pounds  a  day. 
52 

Rule  to  find  the  diameter  of  the  feed  pulley  needed  to  give 
any  number  of  pounds  a  day : 

Multiply  the  number  of  pounds  wanted  by  52,  and  divide  by 
the  product  of  the  weight  of  lap  in  ounces  per  yard,  multiplied  by 
the  R.  P.  M.  of  beater. 

Example :  How  large  a  feed  pulley  will  be  needed  to  produce 
2,250  pounds  a  day,  if  the  lap  weighs  13  ounces  a  yard  and  the 
beater  speed  is  1,500  R.  P.  M.? 

2,250X52 

—  =6  inches,  diameter  of  feed  pulley. 
1,500X13 

In  using  the  above  short  rules  for  production,  remember  that 
the  constant  52  is  figured  for  a.  10  hour  day  with  an  allowance 
of  10  per  cent,  for  loss  of  time. 

ATHERTON   FINISHER   PICKER-  * 

Fig.  7  shows  the  draft  gearing  of  the  Atherton 
finisher  picker.  These  machines  were  formerly  built  by  the  A.  T. 
Atherton  Machine  Co.,  Pawtucket,  R.  I.  The  company  has  since 
sold  out  to  the  Kitson  Machine  Shop,  Lowell,  Mass. 

The  calculation  for  draft  is  given  below,  considering  the 
evener  belt  to  be  working  at  the  middle  of  the  cones,  where  the 
diameter  of  the  two  are  the  same  and  they  have  no  affect  on  the 
draft,  both  running  at  the  same  speed: 

9  X13X15X20X20X22X90X24 

—  =  3.93  draft. 
54X72X52X40X50X  1X7X3 

Omitting  the  draft  gear  of  22  teeth,  but  using  the  remainder 
of  the  formula,  will  give  the  draft  constant : 


PICKERS. 


25 


H  BOTTOM        CALENDER  \ 
fi°Lt-  -r"°>*"-    r 


FIG.  1. 


DIAGRAM  OF  DRAFT  GEARING  OF  ATHERTON  FINISHER 
PICKER. 


9  X13X15X20X20XXX90X24 


—  =  .118  draft  constant. 
54X72X52X40X50X  1X7X3 

In  this  case  a  different  arrangement  is  found  from  the  usual 
rule  in  that  the  draft  gear  occurs  above  the  line.  This  necessi- 
tates a  different  handling  of  the  draft  constant. 

Rule  to  find  draft : 

Multiply  the  draft  constant  by  the  gear. 

Rule  to  find  draft  gear : 

Divide  the  draft  by  the  constant. 

The  knock-off  gearing  used  on  the  Atherton  picker  is  shown 
in  Fig.  8.  The  following  gives  the  length  of  lap,  starting  with  one 
revolution  of  the  knock-off  gear: 


COTTON  MILL  MACHINERY  CALCULATIONS. 


BOTTOM      CAL£ 

NOES?   ROLL 

KNOCK-OFF 


FIG.  8.    DIAGRAM  OF  KNOCK-OFF  GEARING  ON  ATHERTON  PICKER. 


1  X48X28X50X13 


=  45.5  yards  in  lap. 


20X  1  X14X54X1.27 

Leaving  out  the  change  gear  of  20  teeth,  will  give  the  knock- 
off  or  lap  constant. 

1X48X28X50X13 


90.98  constant. 


XX1X14X54X1.27 

This  constant  of  90.98  can  be  used  in  figuring  the  number  of 
yards  in  the  lap  without  making  the  long  calculation,  but  in  this 
case  as  the  change  gear  of  20  teeth  comes  under  the  line,  the 
constant  m-u&t  be  treated  differently  from  the  one  worked  out  on 
the  Kitson  picker. 

Rule  for  using  lap  factor  on  Atherton  pickers : 

Constant  -f-  teeth  in  change  gear  =  number  of  yards  in  lap. 

Constant  -f-  number  of  yards  in  lap  =  number  of  teeth  in 
change  gear. 

HOWARD  AND  BULLOUGH  PICKER. 

A  gearing  plan  of  a  Howard  and  Bullough  intermediate  and 
finisher  picker  is  shown  in  Fig.  9.  The  normal  working  position 
of  the  evener  belt  recommended  by  the  builders  is  about  5  inches 
from  the  large  end  of  the  top  cone.  At  this  point  the  ratio  of  the 
diameters  of  the  two  cones  is  1.6  to  1,  so  we  can  use  this  ratio  in 
place  of  the  actual  diameters.  The  following  figures  give  the 
draft,  treating  the  double  threaded  worm  as  a  gear  of  two  teeth : 


PICKERS. 


27 


rT*r 

c 

BOTTOM      CO/V.£- 

H                    ~ 

'                               

/.« 

TOF>     co/v 


COTTON  MILL  MACHINERY   CALCULATIONS. 
9X12X17X18X27X45X1.6X9X78X24 


=  4.5  draft. 


53X96X60X27X45X1X9X2X12X3 

The  gear  on  the  end  of  the  cross  shaft,  lettered  A,  and  the  one 
on  the  bottom  cone,  lettered  B,  are  both  change  gears,  and,  in 
changing  the  draft,  both  of  these  gears  have  to  be  changed.  The 
sum  of  the  number  of  teeth  in  both  gears  must  always  be  90. 

The  draft  constant  Is  found  as  follows,  leaving  out  the  geare 
A  and  B : 

9X12X17X18X27XXX1.6X9X78X24 

=  4.5  draft  constant. 

53X96X60X27XXX1X9X2X12X2 

Rules  for  finding  the  draft  on  Howard  &  Bullough  pickers : 

Multiply  the  draft  constant  by  the  gear  A,  and  divide  the  re- 
sult by  the  gear  B. 

The  draft  constant  divided  by  the  draft  required  will  equal 
the  change  gear  B  divided  by  the  change  gear  A. 

Example:    What  gears  will  be  needed  to  give  a  draft  of  3.6? 

4.5  H-  3.6  =  1.25. 

Then  B  -f-  A  =  1.25  or  B  must  be  one-fourth  larger  than  A, 
that  is  the  ratio  between  the  two  must  be  5  to  4;  then  B  will 
have  50  teeth  and  A  will  have  40  teeth.  If  the  evener  belt  is 
worked  in  the  middle  of  the  cones,  which  is  the  more  common  rule, 
the  cone  diameters  will  be  equal ;  both  will  run  at  tne  same  speed 
and  have  no  effect  upon  the  draft.  In  this  case  the  draft  will  be 
considerably  reduced,  being  only  2.81  with  the  change  gears  of 
45  teeth  at  A  and  B,  instead  of  a  draft  of  4.5.  The  draft  constant 
in  this  position  of  belt  would  be  2.81.  With  the  cone  belt  at  the 
middle  of  the  cones,  a  draft  of  4  would  call  for  a  53  tooth  gear  at 
A  on  the  bottom  cone,  and  a  37  tooth  gear  at  B  on  the  cross  shaft. 

2.81X53 

—  =  4.02  draft. 
37 

It  is  evident  from  this  that,  except  when  unusual  conditions 
make  it  absolutely  necessary  to  change  these  gears,  they  will  very 
likely  never  be  altered. 

The  lap  gearing  of  the  Howard  &  Bullough  picker  is  so  ar- 
ranged that  the  number  of  teeth  in  the  knock-off  gear  corresponds 
to  the  number  of  yards  in  the  lap.  This  arrangement  is  very 
convenient,  calling  for  no  figuring  to  calculate  the  length  of  lap  or 
of  the  size  of  gear  to  use. 

The  following  short  rule  is  taken  from  the  catalogue  of  the 
Howard  &  Bullough  machines  and  gives  the  pounds  produced  in 


PICKERS. 


a  10  hour  day,  allowing  a  loss  of  10  per  cent,  for  stops,   and    a 
beater  speed  of  1,450  R.  P.  M. : 

Multiply  38.5  by  the  diameter  of  the  feed  pulley  and  this  by 
the  ounces  per  yard  in  the  lap. 


FIG.  10.    DIAGRAM  OF  GEARING  OF  POTTER  &  JOHNSTON  FINISHER 

PICKER. 

POTTER  AND  JOHNSTON  PICKERS. 

The  gearing  diagram  of  the  Potter  &  Johnston  intermediate 
and  finisher  picker  is  shown  in  Fig.  10.  This  is  a  new  machine  on 
the  market.  The  draft  calculation  is  given  below,  considering  the 
evener  belt  to  be  in  the  middle  of  the  cones  or  on  equal  diameters : 

9X12X17X19X12X90X22X12 

=  3.95  draft. 

54X70X83X40X1X9X18X21/16. 

Using  the  above  formula  but  leaving  out  the  draft  gear  of  19 


80 


COTTON  MILL  MACHINERY   CALCULATIONS. 


teeth,  which  comes  above  the  line,  we  get  the  draft  constant : 

9X12X17XXX12X90X22X12 


=  .208  draft  constant. 


54X70X83X40X1X9X18X2  1/16. 

Rule  for  using  draft  constant : 

Constant  multiplied  by  the  gear  will  give  the  draft. 

Draft  divided  by  the  constant  will  give  the  gear. 


SO 



K/£ 

/^ 

t3 

^* 

u*r=>  ftoe-f-     s      O/AA*. 

FIG.  11.    KNOCK-OFF  GEARING  ON  POTTER  &  JOHNSTON  PICKER. 


The  lap  gearing  for  the  Potter  &  Johnston  picker  is  shown  in 
Fig.  11.  The  method  of  finding  the  constant  and  length  of  lap  is 
the  same  as  that  given  above. 

Example:     Find  length  of  lap:  V 

1  X40X34X50X12 

—  =  45.76  yards  in  lap. 
20X  1  X13X54X1.27 

To  find  knock-off  constant: 

1X40X34X50X12 


XX  1  X34X54X1.27 


915.2  constant. 


Rules  for  using  knock-off  factor  on  this  machine: 

Constant  -=-  gear  =  yards  in  lap. 

Constant  -f-  yards  in  lap  =  teeth  in  gear. 

In  operating  any  of  the  foregoing  machines,  the  production 
can  be  easily  calculated  by  using  the  production  constant  of  23.56 
given  above  and  based  on  the  speed  of  the  9  inch  lap  roll  and  the 
weight  of  lap. 

Constant  x  R.  P.  M.  of  lap  roll  x  ounces  per  yard  in  lap  = 
pounds  per  day  of  10  hours,  allowing  20  per  cent,  for  loss  of  time. 


PICKERS. 


31 


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9) 

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5        a 

Q          a) 

-> 


55" 


ooooooooo< 

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,j    <M  <M  oa  <M  co  co  co  eo  **<  • 


d 


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ooooo  o~o  oooo 

OSfNl'^C^-OSr- 1-^O<Ji  — *  T+H 

,±IS^<N<M<NCOCOCOCO^^ 


jS& 


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w  o 


3°  COTTON  MILL  MACHINERY   CALCULATIONS. 

CHAPTER  III. 


CARD   CALCULATIONS — DRAFT — DOFFER   SPEED — USE   OF  DRAFT, 
DOFFER  SPEED  AND  PRODUCTION  CONSTANTS. 

In  looking  at  the  gearing  diagrams  of  the  cards  shown,  it  will 
be  noticed  that  they  are  all  very  similar.  In  all  cases  a  change 
from  a  small  to  a  larger  draft  gear  will  drive  the  feed  roll  faster, 
feeding  in  more  stock  and  thus  decreasing  the  draft  of  the  machine 
and  increasing  the  weight  of  the  sliver  delivered.  An  opposite 
change  would  give  opposite  results.  In  dealing  with  the  draft  con- 
stant of  the  cards  the  following  rules  apply : 

Draft  constant  divided  by  the  draft  equals  the  gear  to  use. 

Draft  constant  divided  by  the  gear  equals  the  draft  of  the 
card. 

In  the  doffer  speed  gearing  we  find  a  similarity.  About  the 
only  noticeable  difference  is  in  the  gearing  between  the  barrow 
pulley  and  the  doffer.  On  all  cards  a  change  from  a  small  to  a 
large  doffer  change  gear  will  drive  the  doffer  faster,  thus  increas- 
ing the  production  of  the  card,  by  causing  it  to  deliver  a  greater 
length  of  sliver,  but  not  affecting  the  weight  of  the  sliver  per  yard. 
This  change  gear  is  also  called  the  production  gear  or  the  speed 
gear,  and  in  all  cases  directly  controls  the  production  of  the  card. 

It  will  be  understood  from  the  above,  that  any  desired  change 
in  the  weight  of  the  card  sliver  will  be  secured  by  a  change  in  the 
size  of  the  draft  change  gear  and  any  change  in  the  total  produc- 
tion of  the  card  will  be  secured  by  a  change  in  the  doffer  change 
gear.  The  following  rules  for  the  use  of  the  doffer  speed  constant 
hold  good  on  all  cards : 

Speed  constant  multiplied  by  the  teeth  in  the  change  gear 
gives  the  speed  of  the  doffer. 

The  doffer  speed  divided  by  the  constant  gives  the  size  gear 
to  use. 

The  standard  speed  for  card  cylinders  is  165  revolutions 
per  minute,  and  in  most  cases  they  are  run  at  this  speed.  The  cyl- 
inders are  built  fifty  inches  in  diameter  and  forty  inches  or  forty 
five  inches  across  the  face.  The  driving  pulleys  are  made  twenty 
inches  in  diameter.  The  draft  of  the  card  varies  from  80  to  125, 
with  100  considered  as  an  average  draft.  The  speed  of  the  doffer 
varies  between  9  and  18  revolutions  per  minute  depending  upon 
the  quality  desired,  the  production  needed  and  the  size  of  the  dof- 
fer, which  may  be  24,  26,  27  or  28  inches  in  diameter.  The  use 
of  the  24  inch  doffer  is  considered  out  of  date  now. 

The  weight  of  the  sliver  run  depends  upon  the  internal  con- 
ditions in  the  mill  and  the  style  or  quality  of  finished  product  and 


CARDS. 


33 


may  be  anywhere  between  35  and  70  grains  per  yard.  Fig.  12 
shows  a  diagram  of  the  gearing  of  the  Saco-Pettee  card  with  27 
inch  doffer  made  by  the  Saco-Pettee- Co.,  Biddeford,  Maine  and 
Newton  Upper  Falls,  Mass.  Using  our  same  method. for  figuring 


FIG.  12.    PLAN  OF  GEARING  ON  THE  SACO-PETTEE  CARD. 


draft  and  working  between  the  2  inch  coiler  calender  roll  and  the 
2^4  inch  feed  roll,  leaving  out  the  draft  gear,  we  get  the  draft  con- 
stant as  follows : 


2  X21X23X214X40X120 
18X17X21X45XXX2.25 


=  1525.09  draft  constant. 


34  COTTON  MILL  MACHINERY   CALCULATIONS. 

Constant 

=  Draft 

Gear 

Constant 

=  Gear. 

Draft 

In  getting  the  speed  of  the  doffer,  start  with  the  cylinder 
speed,  which  is  165  revolutions  per  minute,  and  treat  as  in  any 
ordinary  speed  problem,  remembering  that  the  product  of  *che 
speed  of  the  driver  multiplied  by  its  diameter  must  equal  the  pro- 
duct of  the  speed  of  the  driven  multiplied  by  its  diameter. 

The  following  figures  give  the  speed  of  the  doffer: 

165X18X4X25 

— •  =  11  revolutions  per  minute. 
7X18X214 

To  find  the  doffer  speed  constant,  use  same  method  as  above, 
leaving  out  the  doffer  change  gear  which  was  a  25  tooth  gear. 

165X18X4XX 

—  =  .44  doffer  speed  constant. 
7X18X214 

Constant  x  Gear  =  Speed. 
Speed 


=  Gear. 


Constant 

There  is  always  a  slight  draft  between  the  coiler  calender 
roll  and  the  card  calender  roll,  and  also  between  the  card  calender 
roll  and  the  doffer.  This  draft  or  tension  is  simply  for  the  purpose 
of  keeping  the  cotton  tight  and  preventing  undue  sagging  of  the 
web  or  sliver  at  either  place.  Care  should  be  taken  to  see  'that  this 
tension  is  not  too  much,  as  there  will  be  the  chance  of  stretching 
the  roving  at  places,  which  would  make  it  uneven.  This  tension 
should  be  just  enough  to  keep  the  cotton  up. 

The  draft  and  doffer  change  gears  are  the  only  change  gears 
on  the  card.  There  is  usually  some  point  between  the  coiler  rolls 
and  the  doffer  where  a  change  in  gearing  can  be  made  to  give  the 
desired  tension  to  the  sliver. 

In  Fig.  13  is  shown  a  diagram  of  the  gearing  of  the  Mason 
card  with  a  24  inch  doffer,  made  by  the  Mason  Machine  Works, 
Taunton,  Mass.  Their  27  inch  doffer  card  gearing  is  very  similar 
to  that  shown. 

The  coiler  calender  roll  is  1  11/16  inches  in  diameter,  and  the 
feed  roll  is  2  7/16  inches  in  diameter.  Reducing  these  two  figures 
to  the  same  terms,  we  get  27/16  for  calender  roll  and  39/16  for 


CARDS. 


35 


feed  roll,  and  we  can  use  the  figures  27  and  39  for  the  diameters  of 
the  two  rolls.  With  this  in  mind,  the  draft  constant  may  be  ob- 
tained as  follows : 

27X24X29X190X34X130 

=  1,520  draft  constant. 

18X15X29X34XXX39  , 

To  find  the  doffer  speed  constant: 

165X18X4XX 

=  .595  or  .6  speed  constant. 

7X15X190 


fQO. 


FIG.  as.    PLAN  OF  GEARING  ON  THE  MASON  CARD. 


COTTON  MILL  MACHINERY   CALCULATIONS. 


Fig   14   shows  a  diagram  of  the  gearing  of  the  Whitin  card 
with  a  27  inch  doffer,  made  by  the  Whitin  Machine  Works,  Whit- 


"  D 


-SO  "Of AM. 


FIG.  14.    PLAN  OF  GEARING  ON  THE  WHITIN  CARD. 


insville,  Mass.  It  will  be  noticed  that  between  the  upright  shaft 
and  the  card  calender  roll  there  are  two  gears  of  39  and  38  teeth 
respectively.  This  arrangement  readily  permits  the  variation  of 
the  speed  of  the  coiler  calender  rolls  when  necessary  to  keep  the 
sliver  tight  between  the  two  points. 

The  draft  constant  is  found  as  follows : 

2X36X39X192X160 

- =  2,242  draft  constant. 

18X38X25  XXX  2.25 


CARDS. 


37 


In  the  above  calculation  the  two  16  tooth  bevel  gears  on  the 
ends  of  the  upright  shaft  and  coiler  calender  roll,  and  the  two 


5  O  "  £)  /^\  A/I 


seo 


FIG.  15.    PLAN  OP  GEARING  ON  THE  LOWELL  CARD.    . 

45  tooth  bevel  gears  on  ends  of  doffer  shaft  and  side  shaft,  have 
been  left  out,  as  they  would  have  no  effect  on  the  constant  if  used. 
Where  two  gears  meshing  together  and  having  the  same  number 
of  teeth  appear  in  any  calculation,  both  can  be  disregarded.  The 
doffer  speed  constant  is  obtained  as  follows : 

165X18X4.25XX 

=  .606  speed  constant. 

7X15.5X192 


443971 


38  COTTON  MILL  MACHINERY   CALCULATIONS. 

In  Fig.  15  is  shown  a  diagram  of  the  gearing  of  the  Lowell 
card  with  24  inch  doffer,  made  by  the  Lowell  Machine  Shops, 
Lowell,  Mass.  This  diagram  is  taken  from  the  older  model  of 
card,  their  latest  model  card  having  a  28  inch  doffer,  the  gearing 
of  both  being  very  similar.  The  draft  constant  is  obtained  as  fol- 
lows: 

2.125X31X192X120 

—  =  1,499  draft  constant. 
15X30XXX2.25 

The  following  figures  give  the  doffer  speed  constant : 

165X18X6XXX20 


.552  doffer  speed  constant. 


7X12X40X192 

Fig.  16  shows  a  diagram  of  the  gearing  of  the  Howard  and 
Bullough  card  with  26  inch  doffer,  made  by  Howard  and  Bullough, 
American  Machine  Company,  Ltd.,  Pawtucket,  K.  I.  This  card  is 
built  with  a  26  inch  doffer  only  and  the  gearing  is  similar  to  the 
others.  The  draft  constant  is  found  as  follows : 

2X25X180X120 

—  =  1,579. 
16X19XXX2.25 

The  doffer  speed  constant  is  found  as  follows : 

165X19X6X26XX 


=  .414. 


7X9X104X180 

In  Fig.  17  is  shown  a  diagram  of  the  gearing  of  the  Potter 
and  Johnston  card  with  a  25%  inch  doffer  made  by  Potter  and 
Johnston  Machine  Co.,  Pawtucket,  R.  I.  The  following  figures 
give  the  draft  constant : 

2X32X204X13X120X50 

—  =1,813.33. 
15X32X13  XXX40X2.25 

The  doffer  speed  constant  is  found  as  follows : 

165X25X15XX 


.208  or  .21. 


13.875X105X204 

The  method  used  on  these  cards  for  driving  the  licker-in,  dof- 
fer and  flats  all  with  one  belt,  is  shown  in  Fig.  18.  The  belt  leaves 
the  under  side  of  cylinder  pulley,  goes  over  the  licker-in  pulley, 
then  to  the  doffer  driving  pulley  and  around  the  doffer  grinding 
pulley,  then  up  and  around  the  flat  driving  pulley  and  back  to  the 
cylinder  pulley.  When  the  card  is  working,  the  pulley  on  the  end 
of  doffer  runs  loose  and  serves  only  as  a  binder  pulley  to  carry  the 


CARDS. 


belt  down  and  out  of  the  way.    When  grinding  the  card,  this  pul- 
ley is  fast  and  serves  to  drive  the  doffer  from  the  cylinder. 

In  getting  the  foregoing  draft  constants,  we  have  figured,  in 
every  case,  between  the  feed  roll  and  the  coiler  calender  roll.    In 


JJ 


/eo  — 


3" D 


FIG.  16.    PLAN  OF  GEARING  ON  THE  HOWARD  AND  BULLOUGH 
CARD. 

this  way  the  total  draft  of  the  machine  is  obtained,  with  the  ex- 
ception of  the  slight  tension  always  present  between  the  feed  roll 
and  the  wooden  lap  roll,  but  this  is  too  small  to  affect  the  results 
to  any  great  extent. 

As  mentioned  before,  there  is  aways  a  slight  tension  between 
the  coiler  and  card  calender  rolls,  and  between  the  card  calender 


40 


COTTON  MILL  MACHINERY  CALCULATIONS. 


rolls  and  the  doffer:  Take  the  Lowell  card,  shown  in  Fig.  15,  for 
example,  and  calculate  the  tension  between  the  coiler  and  card 
calender  rolls  as  follows  : 


2.125X31 

- 

15X4 


1.098. 


n 


M=L- 


/e.5   S=?f=>M 
*SO' 


>^"o 


ISO 

flu 


H4 . 


v  20  -g-o 


FIG.  17.    PLAN  OF  GEARING  ON  THE  POTTER  AND  JOHNSTON 
CARD. 


CARDS. 


41 


Find  the  tension  between  the  4  inch  card  calender  roll  and  the 
24  inch  card  doffer  as  follows : 


4X192 


30X24.75 


1.034. 


In  this  calculation  the  diameter  of  the  doffer  is  taken  at  24.75 
inches  or  from  point  of  teeth  to  point  of  teeth  on  opposite  side  of 
doffer,  as  this  is  the  surface  from  which  the  cotton  is  combed. 
The  doffer  measurements  are  always  given  on  the  bare,  surf  ace 
and  the  clothing  is  %  inch  thick,  which  makes  the  additional  % 
inch  added  to  the  doffer  diameter. 

If  these  two  tensions  are  multiplied  together  we  will  get 
1.135  as  the  total  draft  or  tension  between  the  coiler  rolls  and  the 
doffer,  and  if  we  figure  this  tension  from  the  gearing  we  find  that 
the  two  coincide  as  seen  below : 


2.125X31X192 
15X30X24.75 


1.135. 


FIG.  18.    SIDE  VIEW  OF  POTTER  AND  JOHNSTON  CARD  SHOWING 
METHOD  OF  DRIVING  DOFFER,  FLATS  AND  LICKER-IN. 

It  must  be  taken  into  consideration,  that,  in  using  the  draft 
constant  to  get  the  draft  of  a  card,  we  get  the  figured  draft,  that 
is,  the  actual  ratio  between  the  length  of  material  received  and  de- 
livered. This  draft  is  always  less  than  the  actual  draft,  as  ob- 
tained from  the  weights  on  the  front  and  back  of  the  card.  As 
the  actual  draft  is  the  exact  ratio  between  the  weights  at  these 
two  points,  it  must  of  necessity  take  into  consideration  any  loss 
of  material  in  the  form  of  waste  taken  out  by  the  card  as  the  cot- 


42  COTTON  MILL  MACHINERY   CALCULATIONS. 

ton  passes  through.  The  amount  or  per  cent,  of  waste  made  by 
the  card  must  be  deducted  from  the  total  weight  on  the  back  be- 
fore we  can  get  the  exact  weight  of  the  sliver  on  the  front. 

Example:  If  the  lap  on  the  back  of  the  card  weighs  14 
ounces  per  yard,  the  card  makes  5  per  cent,  waste,  the  figured  draft 
is  100,  what  is  the  weight  of  the  sliver?  As  the  sliver  is  expressed 
in  grains  per  yard,  we  must  reduce  the  weight  of  the  lap  to  grains, 
there  being  437.5  grains  in  an  ounce.  Now  to  allow  for  the  waste 
made  we  can  multiply  by  .95,  which  is  the  same  as  getting  5  per 
cent,  of  the  total  and  subtracting  it  from  the  total  weight.  The 
following  figures  will  give  the  weight  of  the  sliver : 

14X437.5X.95 

=  58.19  grains  per  yard. 

100 

Now  if  we  take  the  above  weight  of  sliver  and  divide  it  into 
the  weight  of  the  lap  we  will  get  the  actual  draft  of  the  card : 

14X437.5 

—  =  105.25  as  the  actual  draft. 
58.19 

In  .finding  the  weight  of  the  lap  from  the  weight  of  the  sliver 
on  front  and  the  figured  draft  of  the  card,  the  per  cent,  of  waste 
must  be  taken  into  consideration  just  the  same  as  before. 

Example :  Sliver  weighs  58.19  grains  per  yard,  the  figured 
draft  is  100,  and  the  waste  made  is  5  per  cent.,  what  is  the  weight 
of  lap  on  back? 

58.19X100 

=  14  oz.  lap. 

437.5X.95 

If  we  figure  the  weight  of  lap  from  the  actual  draft  of  105.25 
and  the  weight  of  sliver  obtained  above,  we  get: 

58.19X105.25 

—  =  13.998  oz.  lap.  ' 
437.5 

This  is  close  enough  to  call  a  14  oz.  lap.  The  foregoing  ex- 
amples and  figures  ought  to  make  clear  the  effect  the  waste  has 
on  the  weight  of  the  sliver  and  the  difference  between  figured 
draft,  obtained  from  the  gearing,  and  the  actual  draft,  obtained 
from  the  weight  on  front  and  back  of  the  machine.  Always  bear 
in  mind  that  the  weight  on  the  back  of  the  card  is  100  per 
cent,  or  the  whole;  that  in  figuring  the  weight  on  the  front,  the 
waste  must  be  taken  out  of  the  total  weight  going  into  the  ma- 
chine, unless  we  use  the  actual  draft.  Also  the  weight  on  the  front 
and  the  figured  draft  multiplied  together  will  give  a  certain  per- 
centage of  the  total  weight  on  the  back,  this  percentage  depend- 


CARDS.  43 

ing  upon  the  amount  of  waste  taken  out  during  the  operation  of 
the  machine. 

In  the  above  cases,  the  weight  on  the  back  is  taken  as  100  per 
cent.,  then  the  waste  is  5  per  cent,  and  the  amount  tnat  passes 
through  the  machine  is  95  per  cent.  Consequently  the  weight  of 
the  sliver  multiplied  by  the  figured  draft  will  represent  only  95 
per  cent,  of  the  amount  being  fed  into  the  machine,  the  other  5 
per  cent,  being  waste.  The  two  following  formulas  are  deduced 
from  the  foregoing  remarks  and  examples : 

To  find  the  weight  of  sliver : 

Weight  of  lap  x  437.5  x  .95 

—  =  grains  per  yard  in  sliver. 
Figured  Draft 

To  find  the  weight  of  lap : 
Weight  of  Sliver  x  Figured  Draft 

—  Weight  of  lap  in  ozs. 

437.5  x  .95  [per  yard. 

It  will  be  understood  that  when  the  actual  draft  is  known  in- 
stead of  the  figured  draft,  it  is  simply  a  case  of  dividing  the  weight 
on  the  back  by  the  actual  draft  to  get  the  weight  on  the  front,  and 
the  weight  on  the  front  multiplied  by  the  actual  draft  will  give  the 
weight  on  the  back.  In  the  above  example  the  waste  of  the  card  has 
been  taken  as  5  per  cent.,  as  this  is  considered  a  good  fair  average, 
but  where  the  waste  is  more  or  less,  the  allowance  must  be  made. 
For  instance  if  the  card  is  making  6  per  cent,  of  waste,  use  .94  in 
the  rules  given  in  place  of  the  .95. 

PRODUCTION. 

The  production  of  the  card  depends  upon  the  quality  and 
quantity  of  sliver  desired  and  is  governed  by  the  weight  of  the 
sliver,  the  size  and  speed  of  the  doffer,  and  the  time  lost  due  to 
stripping,  grinding,  etc.  The  amount  of  time  lost,  taking  all  things 
into  consideration,  will  not  be  far  from  10  per  cent,  for  the  whole 
room.  This  is  making  allowance  for  one  card  out  of  every  24  to 
be  stopped  for  grinding. 

The  actual  number  of  pounds  delivered  by  the  card  during  a 
day  may  vary  from  60  to  70  on  fine  work  and  sometimes  below 
these  figures,  to  200  or  over  on  coarse  work.  In  the  former  case, 
quality  is  the  main  consideration,  and  in  the  latter  case  the  con- 
siderations of  quality  have  been  pushed  aside  by  the  demands  of 
quantity.  It  is  useless  to  think  that  the  two  can  go  together,  for 
whichever  one  is  the  most  desired,  the  other  falls  off. 

The  speed  of  the  doffer  affects  the  speed  of  every  part  of  the 


44  COTTON  MILL   MACHINERY   CALCULATIONS. 

card  except  the  cylinder,  licker-in  and  flats.  A  change  in  the  size 
of  the  doffer  gear  has  no  effect  on  the  draft  of  the  machine  or  on 
the  weight  of  the  sliver,  as  an  increase  in  the  doffer  speed  in- 
creases the  speed  of  the  feed  rolls  and  calender  rolls  in  the  same 
proportion,  and  its  only  effect  is  to  put  more  cotton  through  the 
card  in  the  same  time.  Consequently,  the  faster  the  doffer  speed 
the  more  the  card  produces. 

In  working  out  the  production  of  the  card  the  following  rule 
is  used : 

Diameter  of  doffer  x  3.1416  X  speed  of  doffer  x  minutes  per 
day  x  weight  of  sliver  x  allowance  for  loss  of  time  -j-  inches  in 
one  yard  x  grains  in  one  pound. 

Example :  Find  the  production  of  a  card  from  following  data : 
Doffer  27  inches  in  diameter,  doffer  speed  14  revolutions  per 
minute,  weight  of  sliver  50  grains,  working  10  hours  a  day  and 
allowing  10  per  cent,  for  loss  of  time.  Substituting  the  above 
figures  in  the  formula  we  get: 

27.75X3.1416X14X600X50X.90 

- —  =  130.77  pounds. 
36X7,000 

To  be  absolutely  accurate  in  figuring  production  on  the  card, 
we  should  take  the  speed  of  the  coiler  calender  rolls,  as  the  sliver 
is  weighed  after  passing  them  and  is  lighter  than  when  being 
combed  off  of  the  doffer,  due  to  the  influence  of  the  tension  be- 
tween these  points.  The  production  is  more  than  the  figures  just 
obtained,  and  the  difference  will  vary  with  the  varying  amount  of 
tension  between  these  points.  The  only  reason  for  the  use  of  the 
doffer  speed  as  a  basis  .for  production  calculations,  is  that  it  is 
more  easily  determined,  if  not  already  known. 

If  we  take  the  Whitin  card  gearing,  shown  in  Fig.  14,  which 
has  a  27  inch  doffer,  and  calculate  the  speed  of  the  coiler  calender 
rolls,  we  get : 

14X192X39X36 

=  220.7  R.  P.  M.  of  coiler  rolls. 

25X38X18 

Now  take  this  speed  as  a  basis  of  calculation,  figure  the 
production  of  the  card  and  make  the  same  10  per  cent,  allow- 
ance for  loss  of  time,  we  get : 

2X3.1416X220.7X600X50X.90 

•  =  148.57  pounds. 

36X7,000 

Figuring  by  this  method  shows  a  difference  of  17.8  pounds 
in  the  total  production,  or  an  increase  of  the  former  figures  of 
about  13  per  cent.  That  is,  the  production  as  figured  from  doffer 


CARDS.  45 

speed  is  about  13  per  cent,  less  than  the  card  actually  produces, 
and,  unless  some  allowance  is  made  for  this,  all  production  fig- 
ures will  be  too  small. 

If  we  calculate  the  tension  between  the  doffer  and  coiler  cal- 
ender rolls  on  the  card  shown  in  Fig.  14,  we  get : 

2X36X39X192 

—  —  1.128    or   practically    1.13. 
18X38X25X27.75 

That  is,  for  every  yard  combed  off  the  doffer,  1.13  yards  will 
be  delivered  into  the  can,  and  for  every  revolution  of  the  doffer, 
ihere  is  13  per  cent,  more  sliver  put  into  the  can  than  its  circum- 
ference would  indicate.  Therefore,  any  production  calculation 
based  on  doffer  speed  will  necessarily  give  results  that  will  be  too 
little,  unless  this  fact  is  taken  into  consideration. 

The  tensions  between  the  doffer  and  coiler  calender  rolls,  for 
the  different  cards  illustrated  will  be  seen  in  the  following  table 
and  will  indicate  the  per  cent,  of  increase  in  calculating  produc- 
tion in  each  case: 

Fig.  12.  Saco-Pettee,  1.15. 

Fig.  13.  Mason,  1.15. 

Fig.  14.  Whitin,  1.13. 

Fig.  15.  Lowell,  1.135. 

Fig.  16.  Howard  &  Bullough,  1.10. 

Fig.  17.  Potter  &  Johnston,  1.05. 

From  this  table  it  will  be  seen  that,  as  a  general  rule,  13  per 
cent,  must  be  added  to  the  production  when  calculated  upon  a 
basis  of  doffer  speed.  It  must  also  be  understood  that  the  above 
tensions  and  other  drafts  and  speeds  refer  to  the  gearing  shown 
in  the  different  drawings,  and,  unless  the  machine  has  exactly  the 
same  layout  of  gears,  the  results  will  be  different. 

For  use  in  figuring  productions  it  is  convenient  to  have  a 
constant  on  account  of  the  amount  of  time  saved.  In  getting  a 
production  constant  the  same  method  is  followed  as  previously 
dealt  with  on  the  pickers.  On  the  card  the  variable  quantities  in 
the  production  calculation  are  the  speed  of  the  doffer  and  the 
weight  of  the  sliver.  Take  the  figures  used  in  fir  ding  the  pro- 
duction and  eliminate  these  two  quantities,  and  we  get  the  follow- 
ing, which  gives  the  production  constant : 

27.75X3.1416X600X.90 

=  .1868. 

36X7,000 

On  account  of  the  above  explained  tension  or  draft  between 
the  doffer  and  the  coiler  calender  rolls,  this  figure  must  be  increas- 
ed 13  per  cent,  to  give  the  correct  production,  then : 


46  COTTON  MILL   MACHINERY   CALCULATIONS. 

.1868  X  1.13  =  .2111  Production  Constant. 

As  will  be  noticed  this  constant  is  figured  lor  a  10  hour  day, 
allowing  10  per  cent,  loss  of  time  for  oiling,  stripping,  etc. 

Rule  for  finding  the  production,  using  the  production  con- 
stant : 

Production  constant  X  revolutions  per  minute  of  the  doffer  * 
weight  of  sliver  =  pounds  per  day  per  card. 

Example :  What  is  the  production  of  a  card  with  a  27  inch 
doffer,  making  14  revolutions  per  minute  and  delivering  a  50 
grain  sliver? 

.2111  X  14  X  50  =  147.77  pounds. 

The  production  figured  before  with  same  data  resulted  in 
148.57  pounds,  so  it  will  be  seen  that  the  constant  will 
give  results  close  enough  for  all  practical  purposes.  As  there  are 
in  use  cards  with  doffers  of  different  diameters,  there  is  given  be- 
low a  table  of  constants  for  production  for  use  on  cards  that  have 
the  different  size  doffers: 

24  inch  doffer,  .1877  production  constant. 

26  inch  doffer,  .1980  production  constant. 

27  inch  doffer,  .2111  production  constant. 

28  inch  doffer,  .2187  production  constant. 

In  all  the  above  an  allowance  of  10  per  cent,  loss  of  time  has 
been  made,  and  10  hours  is  considered  as  a  day ;  allowance  also  has 
been  made  in  the  figures  for  the  tension  between  the  doffer  and  the 
coiler  calender  rolls.  In  making  changes  in  the  drafts  and  speeds 
of  a  card  the  calculations  can  be  conveniently  and  quickly  made 
by  proportion,  as  illustrated  by  the  following  rules. 

Rule  to  change  the  weight  of  the  sliver : 

Multiply  the  weight  of  the  sliver  wanted  by  the  gear  on  the 
card  and  divide  the  product  by  the  weight  of  the  sliver  on  thet 
card.  Answer  will  be  the  size  gear  to  use. 

Example:  A  card  is  running  a  50  grain  sliver  with  a  16 
tooth  draft  gear.  What  size  gear  will  have  to  be  used  to  change  the 
sliver  to  56  grains  ? 

56X16 

—  =  17.9  or  18  tooth  draft  gea^ 
50 

Also  in  dealing  with  the  draft  and  weight  instead  of  gear  and 
weight : 

Multiply  the  draft  by  the  weight  on  the  card  and  divide  by 
the  weight  wanted.  Answer  will  be  the  draft  needed. 

In  changing  the  draft  of  the  card,  use  the  following  rule : 

Multiply  the  draft  of  the  card  by  the  draft  gear  and  divide 


CARDS.  47 

by  the  draft  ivanted.    Ansiver  will  be  the  draft  gear  needed. 

Rule  to  change  doffer  speed: 

Multiply  the  desired  speed  of  doffer  by  the  change  gear  on 
the  card  and  divide  by  the  present  doffer  speed.  Answer  will  be 
the  size  gear  needed. 

Rule  to  change  the  production  of  the  card : 

Multiply  the  speed  of  the  doffer  by  the  production  wanted 
and  divide  by  the  present  production  of  the  card.  Answer  will  be 
the  required  speed  of  the  doffer. 

The  production  of  the  card  can  be  changed  from  the  size  of 
the  doffer  gear  direct,  by  putting  in  the  above  rule  the  size  of 
the  change  gear  in  place  of  the  doffer  speed. 

Example:  A  card  is  producing  160  pounds  per  day  with  a 
26  tooth  doffer  change  gear.  What  size  gear  will  be  needed  to  give 
a  production  of  135  pounds  per  day? 

26X135 

—  ==  21.9  or  22  tooth  doffer  change  gear. 
160 


4S 


COTTON  MILL  MACHINERY   CALCULATIONS. 


Showii 


CARD    DRAFT    TABLE 

the  Figured  Draft  for  Different  Weights  of  Sliver  and  Lap 
Allowance  of  5  per  cent  Waste  has  been  made 


Ounces 
Per 
Yard 

L^p 

GRAINS  PER  YARD  IN  SLIVER 

40 

42 

44 

46 

48 

50 

52 

54 

56J58 

60 

62 

64 

66 

68 

70 

72 

74 

10 

104 

99 

95 

91 

87 

83 

80 

77 

74 

10.5 

109 

104 

99 

95 

91 

87 

84 

81 

78 

75 

11 

114 

109 

104 

91) 

95 

91 

S8 

86 

82 

79 

76 

74 

11.5 

119 

114 

109 

104 

100 

96 

92 

89 

86 

83 

80 

77 

75 

12 

125 

119 

114 

109 

104 

100 

96 

92 

89 

86 

83 

80 

78 

76 

12.5 

124 

119 

114 

10!) 

104 

100 

96 

98 

90 

87 

84 

81 

79 

76 

13 

123 

118 

113 

108 

104 

100 

96 

93 

90 

87 

85 

82 

79 

77 

13.5 

122 

117 

112 

108 

104 

100 

97 

94 

90 

87 

85 

83 

HO 

78 

14 

121 

116 

112 

108 

104 

100 

97 

94 

91 

87 

85 

83 

81 

79 

14.5 

121 

11(5 

112 

108 

104 

100 

97 

94 

91 

89 

86 

84 

81 

15 

125 

120 

115 

111 

107 

104 

101 

97 

94 

92 

89 

86 

84 

15.5 

124 

120 

115 

111 

107 

104 

101 

98 

95 

92 

89 

87 

16 

12.'-! 

119 

115 

111 

107 

104 

101 

98 

95 

92 

90 

16.5 

122 

118 

114 

111 

107 

104 

101 

98 

95 

93 

17 

122 

118 

114 

110 

107 

104 

101 

98 

95 

CARDS. 


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50  COTTON   MILL  MACHINERY   CALCULATIONS. 

CHAPTER  IV. 


COMBING  PROCESS — CALCULATIONS  FOR  DRAFT,  SPEED  AND  PRO- 
DUCTION ON  SLIVER  AND  RIBBON  LAPPERS — COMBERS,  DRAFT, 
PRODUCTION  AND  WASTE  CALCULATIONS — PRODUCTION  CON- 
STANTS. 

THE  COMBING  PROCESS. 

In  the  manufacture  of  the  finer  grades  of  cotton  yarns  in- 
tended for  the  hosiery  and  underwear  trade,  for  the  better  grades 
of  cotton  dress  goods,  for  mercerizing,  for  crochet  and  em- 
broidery cottons  and  for  the  manufacture  of  lace  and  sewing 
thread,  the  cotton  is  passed  through  another  process  of  cleaning 
after  the  carding,  known  as  combing.  This  is  intended  for  use 


FIG.  19.    GEARING  PLAN  OF  WHITIN  SLIVER  LAPPER. 


only  in  those  mills  that  are  making  a  class  of  product  that  is  de- 
sired to  be  exceptionally  smooth  and  clean  and,  on  the  coarser 
grades  of  work,  it  is  entirely  too  expensive  and  not  necessary  to 
use.  Only  where  the  cost  of  production  is  secondary  to  the  qual- 


COMBING. 


51 


ity  of  the  finished  product  is  it  possible  to  use  the  combing  pro- 
cess to  advantage. 

There  are  usually  three  machines  used  in  combing,  the  sliver 
lapper,  the  ribbon  lapper  and  the  comber.  The  first  two  are  sim< 
ply  -preparatory  machines  and  are  used  for  the  purpose  of  getting 
the  fibers  in  a  parallel  condition  and  putting  the  material  in  a 
suitable  shape  for  use  on  the  comber,  while  the  last  does  the  real 
work  of  cleaning. 

THE  SLIVER  LAPPER. 

The  object  of  the  sliver  lapper  is  to  take  from  12  to  20  card 


FIG.  20.    PLAN  OF  GEARING  ON  MASON  SLIVER  LAPPER. 


52  COTTON   MILL  MACHINERY   CALCULATIONS. 

slivers,  give  them  a  draft  of  from  1.5  to  3.5  and  combine  them 
into  a  smooth,  even  sheet  or  lap  and  wind  this  lap  upon  a  wooden 
spool  for  use  on  the  ribbon  lapper.  The  drawing  bringing  the  fi- 
ber into  parallelism. 

Stop-motions  are  provided  which  operate  to  stop  the  frame 
when  one  end  breaks  or  runs  out  at  the  back,  and  also  when  the 
lap  reaches  a  certain  size,  thus  preventing  singles  at  the  back  and 
making  all  laps  approximately  the  same  length. 

The  drawing  is  accomplished  by  means  of  three  or  four 
pairs  of  drawing  rolls  arranged  for  common  or  metallic  rolls  and, 
in  operation  and  care,  similar  to  those  in  use  on  drawing  frames. 
In  fact  both  the  sliver  and  ribbon  lappers  can  be  considered  as 
modified  drawing  frames.  Fig.  19  shows  a  diagram  of  the  gear- 
ing of  the  sliver  lapper  built  by  the  Whitin  Machine  Works,  gear- 
ed for  use  with  leather  rolls.  This  machine  has  four  pairs  of 
drawing  rolls,  which  distributes  the  total  draft  more  widely  than 
would  be  the  case  with  three  rolls. 

With  a  30  tooth  draft  gear  and  figuring  the  draft  between  the 
IG1^  inch  lap  roll  and  the  l1/^  inch  back  drawing  roll,  we  get  the 
draft,  as  follows: 

16.25X21X50X20X26X23X72 

—  =  2.342    total    draft. 
68X50X20X50X41X30X1.5 

Using  the  above  formula,  but  leaving  out  the  30  tooth  draft 
gear,  we  get  the  draft  constant,  as  follows: 

16.25X21X50X20X26X23X72 

—  =  70.267  draft  constant. 
68X50X20X50X41XXX1.5 

Constant  -+-  gear  =  draft.  Then :  70.267  -j-  30  =  2.342  draft. 

The  above  total  draft  is  distributed  or  divided  into  five  inter- 
mediate drafts,  as  follows: 

(1)  Draft  between  back  and  third  drawing  rolls; 

(2)  Draft  between  third  and  second  drawing  rolls; 

(3)  Draft  between  second  and  front  drawing  rolls; 

(4)  Draft  between  front  drawing  roll    and    the    calender 
rolls ; 

(5)  Draft  between  the  calender  rolls  and  the  lap  rolls. 
The  first  three  of  the  above  intermediate  drafts  are  the  ones 

that  perform  the  real  reduction  in  the  bulk  or  weight  of  the  mate- 
rial, while  the  last  two  serve  simply  to  keep  the  material  tight,  and 
in  no  case  should  be  enough  to  stretch  the  lap.  The  break  draft,  or 
the  one  that  is  altered  when  a  change  is  made  in  the  total  draft,  is 
between  the  front  and  second  drawing  rolls,  the  other  drafts  re- 


COMBING.  53 

maining  the  same  regardless  of  any  change  made    in   the   total 
draft. 

Fig.  20  shows  a  diagram  of  the  gearing  of  the  sliver  lapper 
built  by  the  Mason  Machine  Works.  This  machine  is  built  on  the 
same  principles  as  and  is  similar  to  the  one  shown  in  Fig.  19,  but 
has  three  drawing  rolls.  Using  a  50  tooth  draft  change  gear  on  the 
back  roll,  the  following  gives  the  draft : 

12X12X72X20X28X20X50 

—  =  2.28   draft. 
72X29X20X50X40X22X1.375 

By  leaving  out  the  50  tooth  draft  gear  in  the  above  formula, 
we  get  the  draft  constant  as  follows : 

12X12X72X20X28X20XX 

—  =  .0496   draft   constant. 
72X29X20X50X40X22X1.375 

In  any  arrangement  of  this  kind,  where  the  draft  gear  is  a 
driven  gear,  it  will  come  above  the  line  in  the  formula  for  draft, 
and  must  be  treated  in  a  different  manner  from  the  one  just  work- 
ed out.  In  this  case  the  rules  for  using  the  draft  constant  will  be : 

Constant  X  gear  =  draft. 

Draft  -f-  constant  =  gear. 

Example :  Given  a  draft  constant  of  .0496,  what  draft  will  a 
50  tooth  draft  gear  give? 

.0496  X  50  =  2.28   draft. 


PRODUCTION. 


On  either  of  the  above  machines  the  production  varies  great- 
ly, depending  upon  the  speed  at  which  they  are  run  and  the 
weight  of  the  lap  produced.  The  laps  vary  in  weight  from  250  to 
450  grains  per  yard,  and  the  5  inch  calender  rolls  vary  in  speed 
from  60  to  120  revolutions  per  minute,  which  would  give  a  front 
drawing  roll  speed  of  200  to  450  revolutions  per  minute.  This 
would  make  the  production  vary  from  500  to  1,500  pounds  per 
day  of  10  hours,  allowing  for  25  per  cent,  loss  of  time  due  to  stop- 
pages, etc.  Basing  the  production  on  the  speed  of  the  calender  rolls, 
the  method  of  figuring  would  be  as  follows : 

Example :  What  would  be  the  production  of  a  sliver  lapper, 
if  the  calender  rolls  were  making  100  revolutions  per  minate,  the 
lap  weighing  350  grains  per  yard,  and  allowing  for  25  per  cent, 
loss  of  time,  in  a  10  hour  day? 

5X3. 1416X100  X  600  X350X.75 

—  =  981.75  pounds. 
36X7,000 


54  COTTON  MILL  MACHINERY   CALCULATIONS. 

/ 

In  determining  the  speed  of  the  driving  pulleys  on  the  ma- 
chines we  must  take  into  consideration  the  ratio  in  kpeed  between 
the  calender  rolls  and  the  driving  shaft.  On  the  Whitin  frame, 
£C£rcd  as  shown  in  Fig.  19,  one  revolution  of  the  driving  pulley 
gives  one  revolution  to  the  calender  rolls ;  so  the  speed  of  the  two 
will  be  the  same.  On  the  Mason  frame,  as  shown  in  Fig.  20,  it  takes 
2.48  revolutions  of  driving  pulley  to  give  the  calender  rolls  one 
revolution,  so  that  the  speed  of  the  driving  pulley  will  equal  the 
speed  of  the  calender  rolls  multiplied  by  2.48.  With  this  in  view 
the  following  calculations  for  getting  the  size  of  the  pulleys  need- 
ed to  run  the  machines  will  be  understood. 

Example :  If  the  main  line  shafting  has  a  speed  of  325  revo- 
lutions per  minute,  what  size  pulley  is  needed  to  drive  the  calen- 
der rolls  of  a  Whitin  sliver  lapper  at  100  revolutions  per  minute, 
the  driving  pulley  on  the  machine  being  19  inches  in  diameter? 

100X19 

—5.85  inches,  or  about  a  6  inch  pulley  is  needed. 

325 

Example :  Find  the  size  of  pulley  to  drive  the  calender  rolls 
on  a  Mason  machine  at  100  revolutions  per  minute?  In  this  case  we 
must  multiply  the  speed  of  the  calender  rolls  by  2.48  to  get  the 
speed  of  the  driving  pulleys. 

2.48X100X12 

=  9.15  inches,  or  about  a  9.25  inch  pulley. 

325 

THE  RIBBON  LAPPER. 
/ 

The  object  of  the  ribbon  lapper  is  to  further  prepare  the  laps 
for  the  comber  so  that  they  will  be  of  a  more  uniform  structure 
than  is  possible  with  the  sliver  lapper,  thus  placing  the  fibers  in 
a  better  condition  for  the  combing  by  the  needles  of  the  comber. 
It  is  usually  made  to  double  six  laps,  though  sometimes  only  four 
laps  are  used.  The  average  draft  is  six,  though  we  must  consider 
the  weight  of  finished  laps  desired.  Each  lap  is  drawn  by 
separate  drawing  rollers  and  placed  one  above  the  other  on  the 
sliver  plate,  where  they  are  condensed  and  calendered  by  the  calen- 
der rolls  and  wound  up  in  the  form  of  a  lap  at  the  end  of  the  ma- 
chine. The  laps  are  made  8  to  12  inches  wide,  depending  upon 
the  width  of  lap  the  comber  can  handle.  Stop  motions  are  provid- 
ed to  stop  the  machine  when  a  lap  runs  out,  thus  preventing  sin- 
gles, and  also  when  the  laps  are  full,  thus  insuring  the  laps  to  be 
of  uniform  length.  Leather  or  metallic  rolls  may  be  used  for 
drawing,  though  the  common  preference  seems  to  be  for  leather 
rolls  on  both  the  sliver  and  ribbon  lappers. 

Fig.  21   shows  a  diagram  of  the  gearing  of  the  Whitin  ribbon 


COMBING. 


55 


lapper.  The  arrangement  of  the  draft  rolls  and  gearing  is  very 
similar  to  that  in  use  on  the  drawing  frame.  The  draft  gear,  as 
shown,  is  located  on  the  stud  with  the  100  tooth  gear,  called  the 
crown  gear,  which  is  driven  from  the  front  roll.  The  diagram 
shows  only  one  set  of  drawing  rolls,  the  others  being  simply  a 
continuation  of  those  shown. 


FIG.  21.    GEARING  PLAN  OF  WHITIN  RIBBON  LAPPER. 


Starting  with  the  IG1/^  inch  lap  roll  and  figuring  back  to  the 
2%  inch  wooden  lap  rolls,  we  get  the  following  as  the  draft  con- 
stant : 


16.25X21X16X60X100X70X56 
68X48X80X25XXX25X2.75 


=  286    draft   constant. 


Constant  -=-  gear  =  draft.  Then:  286  -f-  50  =  5.72  draft 
with  a  50  tooth  draft  gear  on  the  machine. 

The  drafts  occurring  between  the  different  drawing  rolls  are 
the  ones  that  do  the  real  reduction  of  the  bulk  of  the  material,  the 
others  being,  in  each  case,  just  enough  to  keep  the  material  tight. 

Fig.  22  shows  a  diagram  of  the  gearing  of  the  Mason  ribbon 
lapper.  This  machine  is  built  on  the  same  principle  as  the  one 
shown  in  Fig.  21.  The  draft  factor,  figuring  between  the  12  inch 
lap  rolls  and  the  2%  inch  wooden  lap  rolls  on  the  back,  is  obtained 
as  follows : 


5f 


COTTON   MILL   MACHINERY   CALCULATIONS. 


12X21X14X19X68X100X70X56 


=  300.78 


or      practically      301      draft 
[constant. 


50X20X40X72  X25XXX30X2.75 

Constant  -+-  gear  =  draft.    Constant  -f-  draft  =  gear. 
Then  a  50  tooth  draft  gear  would  give  a  draft  of  6.02,  as  fol- 
lows : .  301  -7-  50  =  6.02  draft. 

PRODUCTION. 

On  these  two  machines  the  production  varies  greatly,  de- 
pending upon  the  speed  at  which  the  machine  is  run  and  the 
weight  of  the  lap.  The  same  remarks  made  in  reference  to  the 
sliver  lap  machines  can  apply  here,  as  regards  speeds,  etc.,  and, 


FIG.  22.    GEARING  PLAN  OF  MASON  RIBBON  LAPPER. 


as  the  same  size  calender  rolls  are  used  on  all,  the  same  figures  for 
getting  production  will  apply. 

Both  the  Whitin  and  Mason  ribbon  lappers  are  constructed 
to  give  three  revolutions  to  the  driving  pulley  to  one  revolution 
of  the  5  inch  calender  rolls ;  so  the  speed  of  the  driving  pulley  on 
either  must  be  three  times  the  speed  of  the  calender  rolls.  Both 
machines  have  16  inch  driving  pulley ;  so  the  following  calcula- 
tions for  the  size  pulley  needed  to  drive  the  machines  will  apply 
to  both. 

Example :  What  size  pulley  will  be  reqired  to  drive  the  rib- 
bon lapper,  if  the  calender  roll  speed  is  to  be  100  revolutions  per 
minute  and  line  shafting  speed  is  325  revolutions  per  minute? 

3X100X16 

=  14.76  inches,  size  of  pulley. 

325 


COMBING.  57 

The  production  formula  and  calender  roll  diameter  being  the 
same  on  all  the  machines,  and  allowing  a  loss  of  time  of  25  per 
cent.,  a  production  constant  can  be  worked  out  that  will  be  appli- 
cable to  any  one  of  the  four  machines  shown.  The  production  cal- 
culation for  the  sliver  lapper,  previously  given  in  this  chapter,  is 
identical  with  a  production  calculation  for  the  ribbon  lapper.  A 
look  at  this  calculation  will  show  that  there  are  only  two  quanti- 
ties in  which  we  may  expect  to  find  any  variation,  that  is,  the 
speed  of  the  calender  rolls,  given  as  100  revolutions  per  minute, 
and  the  weight  of  the  lap,  given  as  350  grains  per  yard.  So  then, 
if  we  eliminate  these  two  variable  figures  from  the  calculation, 
we  get  the  production  constant  as  follows : 

5  X  3. 1416  X  600  X. 75 

—  =  .028  production  constant. 
36X7,000 

This  constant  of  .'028  multiplied  by  the  speed  of  the  calender 
rolls  and  the  weight  of  the  lap,  will  give  the  production  of  either 
of  the  machines,  based  on  a  10  hour  day  and  allowing  for  25  per 
cent,  loss  of  time.  Then  .028  x  100  x  350  =  980  pounds.  This  cor- 
resopnds  closely  with  the  production  figured  by  the  former  figures. 

As  both  the  sliver  and  ribbon  lappers  are,  in  principle  and 
action,  only  types  of  drawing  frames,  and  subject  the  cotton  to 
the  same  treatment,  the  speed  of  the  front  drawing  rolls  should 
be  about  the  same  as  that  on  the  drawing  frame.  To  get  the  best 
results,  as  regards  good,  even  drawing,  the  front  roll  speed  should 
be  under  375  revolutions  per  minute.  From  Fig.  19  the  following 
speed  ratio  is  found : 

1X50X41 

=  3.428 

26X23 

which  shows  that  the  front  drawing  roll  makes  3.428  revolutions 
to  every  one  revolution  of  the  calender  roll.  Now,  if  the  calender 
roll  speed  is  100  revolutions  per  minute,  the  front  drawing  roll 
will  have  a  speed  of  342.8  revolutions  per  minute,  or  3.428  jtimes 
the  speed  of  the  calender  roll.  This  ratio  can  be  determined  for 
any  machine  and  enables  us  to  find  the  front  roll  speed  for  any 
given  calender  roll  speed. 

THE  COMBER. 

The  cotton,  having  been  placed  in  laps  of  the  proper  size  and 
weight  and  the  fibers  thoroughly  paralleled  by  the  two  former 
machines,  is  now  placed  on  the  lap  rolls  of  the  comber,  slowly 
unwound  and  fed  into  the  machine,  which  combs  out  all  the  trash, 
neps,  motes  and  short  fiber.  The  comber  has  six  or  eight  heads, 
combing  six  or  eight  laps,  each  lap  being  combed  separately,  and 


58  COTTON  MILL  MACHINERY   CALCULATIONS. 

the  webs  from  these  heads  are  condensed  and  formed  into  separate 
slivers.  These  slivers  are  passed  along  a  sliver  plate  at  the  front 
of  the  machine  and  delivered  to  the  draw-box,  which  has  three 
or  four  pairs  of  drawing  rolls,  fitted  with  leather  or  metallic  rolls, 
the  use  of  leather  rolls  being  more  common. 

Here  these  individual  slivers  are  drawn,  condensed  and 
formed  into  a  single  sliver  which  is  passed  up  to  the  coiler  head 
and  delivered  to  the  can.  After  passing  through  the  comber  the 
slivers  are  usually  given  one  or  two  drawings  before  being  ready 
for  the  slubbers. 

Fig.  23  shows  a  diagram  of  the  gearing  of  the  late  model 
Whitin  high  speed  comber.  This  machine  is  built  for  higher  speeds 
than  the  older  models  and  will  do  good  work  at  125  to  135  nips 
per  minute,  thus  greatly  increasing  the  production  over  what  was 
formerly  obtained. 

The  feed  rolls  are  driven  by  a  pin  on' the  main,  or  cylinder 
shaft,  which  works  into  a  5  pointed  star-wheel.  This  gives  the 
star-wheel  1/5  of  a  revolution  for  every  one  of  the  cylinder  shaft. 
On  the  same  stud  with  the  star-wheel  is  the  draft  gear  of  14 
to  20  teeth,  which  drives  the  feed  roll  gear  of  44  teeth.  The  feed 
roll  drives  the  2%  inch  wooden  lap  rolls.  The  draft  gear  is 
changed  to  alter  the  total  draft  of  the  machine.  The  driving  shaft 
carries  a  30  tooth  gear  which,  by  means  of  the  69  tooth  interme- 
diate gear,  drives  the  80  tooth  gear  on  the  cam  shaft.  The  cam 
shaft  drives  the  table  calender  roll  shaft  by  a  21  to  a  142  tooth 
gear.  This  21  tooth  gear  is  changeable  to  regulate  the  tension  on 
the  web  in  the  pans. 

The  draw-box  has  a  set  of  four  drawing  rolls,  the  draft  at 
this  point  being  5.  The  gear  on  the  back  roll  of  the  draw-box  is 
changeable  to  permit  the  regulation  of  the  tension  on  the  slivers 
on  the  sliver  plate.  The  small  gear  of  27  teeth  on  the  driven  end 
of  the  front  roll  is  a  change  gear,  which  gives  a  change  in  the 
draft  of  the  draw-box.  Any  change  of  this  gear  gives  a  change 
in  the  length  of  sliver  fed  out  of  the  draw-box,  and  necessitates  a 
change  in  the  size  of  the  50  tooth  coiler  connecting  gear  which 
drives  the  coiler  upright  shaft,  to  enable  the  coiler  calender  rolls 
to  take  up  the  sliver  delivered  by  the  draw-box.  This  gear  may 
vary  from  25  to  75  teeth. 

It  is  understood  that  it  is  usual  to  change  only  the  draft  gear, 
for,  after  the  tensions  between  the  other  points  have  been  regu- 
lated and  adjusted,  no  further  changes  are  usually  made  in  them. 
The  draft  constant  of  this  comber,  figuring  between  the  2  inch 
coiler  calender  rolls  and  the  2%  inch  wooden  lap  rolls,  is  found  as 
follows : 


COMBING.  59 

2X16X22X60X5X44X23X55X47 


•=-709. 


16X22  X50X1XXX23X20X35X2.75 

With  a  17  tooth  draft  gear  the  total  draft  would  be 
709  ~  17  =  41.3.  This,  of  course,  is  figured  draft  and  is  less  than 
the  actual  draft  by  a  variable  amount,  depending  upon  the  amount 
of  waste  taken  out  by  the  machine. 

The  above  total  draft  is  distributed  over  several  points,  the 
main  portions  being  between  the  feed  rolls  and  the  table  calender 
rolls,  where  the  combing  takes  place,  and  in  the  draw  box,  where 
the  combed  slivers  are  drawn  and  .condensed  into  a  single  sliver. 
These  are  the  points  where  the  real  reduction  in  bulk  of  material 
occurs,  the  others  having  just  enough  draft  or  tension  to  keep  the 
material  tight. 

Fig.  24  shows  a  diagram  of  the  comber  built  by  the  Mason 
Machine  Works.  In  general  arrangement  it  is  similar  to  the  one 
shown  in  Fig.  23.  In  figuring  the  draft  between  the  1  11/16  inch 
eciler  calender  rolls  and  the  2%  inch  lap  rolls,  we  can  simplify 
matters  by  reducing  both  diameters  to  sixteenths,  in  which  case 
they  would  be  27/16  as  diameter  of  the  first  and  44/16  as  diameter 
©f  the  latter.  Now  we  can  use  the  two  numbers,  27  and  44,  to 
represent  the  diameters  of  the  two  rolls.  Then  the  following  gives 
the  draft: 

27X24X21X53X5X38X23X55X47 

=  26.1 

18X16X90X1X17X23X20X35X44 

By  using  the  above  figures  with  the  exception  of  the  17  tooth 
draft  gear,  which  comes  under  the  line,  we  get  a  draft  constant 
of  443.7. 

Constant -=- gear  =  draft,  as  follows:  443.7-^17  =  26.1 
draft. 

In  order  to  ascertain  the  proportion  of  the  total  draft  that 
cccurs  at  the  combing  operation,  we  will  figure  the  draft  between 
the  2%  inch  table  calender  rolls  and  the  feed  roll  as  follows : 

2.75X19X80X5X38 

=  5.48  draft. 

142X80X1X17X.75 

The  draft  between  the  2%  inch  draw-box  calender  rolls  and 
tfee  11/8  inch  draw-box  back  roll  is: 

2.75X20X45X50X46 


4.41  draft. 


43X37X45X16X1.125 

Following  the  same  method,  the  tensions  can  be  figured  be- 
tween the  other  points  on  the  machine,  and  the  product  of  all  the 
intermediate  drafts  will  equal  the  total  draft. 


6C 


COTTON  MILL  MACHINERY   CALCULATIONS. 


COMBING.  61 

In  figuring  the  weight  of  sliver  delivered  by  the  comber  from 
the  draft  of  the  machine  and  the  weight  of  the  laps,  the  percentage 
of  waste  made  must  be  taken  into  consideration,  as  the  draft 
just  obtained  is  figured  draft  and  does  not  take  into  consideration 
the  amount  of  cotton  taken  out  in  the  form  of  waste.  On  the 
isliver  and  ribbon  lappers  there  is  no  loss  of  material  as  waste,  and 
kence  the  actual  and  figured  draft  will  be  practically  the  same. 

On  the  comber  the  waste  varies  from  10  to  25  per  cent,  and 
will  have  a  corresponding  varying  effect  upon  the  weight  of  the 
finished  sliver.  For  example,  take  a  comber  with  six  laps  up,  a 
ftgured  draft  of  30  and  making  20  per  cent,  waste.  If  the  laps 
weigh  300  grains  per  yard,  what  will  the  sliver  weigh? 

The  total  weight  entering  the  machine  will  be  6  x  300  =  1,800 
grains.  Now,  if  there  is  no  waste  made,  1,800  -4-  30  =  60  grains 
per  yard  as  the  weight  of  the  finished  sliver.  But,  of  the  total 
1,800  grains  entering  the  machine,  20  per  cent  is  lost  or  taken  out 
a«  waste,  leaving  only  1,440  grains  to  be  delivered  in  the  form 
of  sliver.  Then :  1,440  -=-  30  =  48  grains  per  yard  as  the  weight 
the  finished  sliver.  With  the  above  figures  for  weight  of  lap  and 
sliver  we  can  figure  the  actual  draft  as  follows: 

6X300 

=  37.5  actual  draft. 

48 

Then  it  will  be  seen  that  a  figured  draft  of  30  with  a  20  per 
cent,  loss  in  waste  will  give  an  actual  draft  of  37.5.  There  are 
several  ways  of  determining  the  per  cent,  of  waste  made,  but  the 
following  is  about  as  short  and  easy  as  any: 

Find  the  figured  draft  from  draft  gear  and  draft  factor. 
Find  actual  draft  from  weight  of  sliver  and  weight  of  lap.  Divide 
the  figured  draft  by  the  actual  draft  and  subtract  the  answer  from 
t>ne. 

Example:  With  comber  which  is  geared  to  give  a  figured 
draft  of  30  and  which  has  an  actual  draft  of  37.5,  what  is  the  per 
cent,  of  waste  being  made? 

30  -f-  37.5  =  .80.     1  —  .80  =  .20  or  20  per  cent  of  waste. 

Example :  What  would  have  to  be  the  weight  of  laps  to  use 
en  a  comber  that  is  delivering  a  48  grain  sliver,  using  a  figured 
draft  of  30,  making  20  per  cent,  waste  and  doubling  six  laps  on 
the  back? 

48X30 

—  =  300  grains  per  yard. 
6X.80 


COTTON  MILL  MACHINERY   CALCULATIONS, 
i — i 


COMBING.  63 

PRODUCTION. 

The  production  of  the  comber  depends  upon  the  speed  of  the 
machine,  or  nips  per  minute,  and  the  weight  of  the  finished  sliver. 
Where  the  best  quality  of  finished  product  is  desired,  it  is  not 
good  policy  to  use  too  high  a  speed  or  too  heavy  a  sliver,  as  the 
machine  cannot  do  good  work  under  these  conditions.  The 
Whitin  high-speed  comber  is  capable  of  making  100  to  140  revo- 
lutions per  minute,  delivering  a  sliver  varying  from  40  to  75 
grains  per  yard,  which  gives  a  total  production  of  68  to  181 
pounds  per  day. 

In  figuring  the  production  from  the  nips  per  minute,  we  must 
figure  out  the  ratio  in  speed  between  the  cylinder  shaft  and  the 
eoiler  calender  rolls,  as  the  latter  is  the  real  delivery  point  of  the 
machine  and  the  production  depends  upon  the  weight  of  finished 
siver  and  the  speed  of  the  calender  rolls.  On  the  single  nip  machine, 
shown  in  diagram,  the  cylinder  speed  and  nips  per  minute  are 
the  same,  while  on  a  duplex  or  double  nip  comber  the  cylinder 
speed  is  one-half  the  number  of  nips.  The  ratio  between  the  cylin- 
der speed  and  the  eoiler  calender  rolls,  using  gears  in  Fig.  23,  is : 

1X60X22X16 

—  =  1.2 
50X22X16 

Then  the  cylinder  speed  or  nips  per  minute  multiplied  by  this 
ratio  of  1.2  will  give  the  speed  of  the  eoiler  calender  rolls.  As 
before  stated,  the  speed  of  the  eoiler  rolls  is  regulated  by  a  change 
gear,  and  any  change  made  in  the  size  of  this  gear  will  change  the 
speed  of  the  eoiler  calender  rolls  and  necessitate  a  new  calculation 
for  a  ratio  between  these  points. 

Example :  What  would  be  the  production  in  a  10  hour  day 
on  a  Whitin  comber,  geared  as  shown  in  Fig.  23,  running  at  a 
speed  of  120  nips  per  minute,  delivering  a  50  grain  sliver,  and 
allowing  for  a  loss  of  time  of  5  per  cent.  ? 

120X1.2  X2X3.1416X600X50X.95 

=  102.32  Ibs. 

36X7,000 

In  the  above  example  the  nips  per  minute  are  multiplied  by 
the  ratio  of  1.2,  and  this  gives  the  eoiler  calender  roll  speed,  the 
other  figures  being  what  we  ordinarily  expect  in  such  a  calcula- 
tion. In  the  above,  we  can  consider  that  the  speed  of  the  machine 
and -the  weight  of  the  sliver  are  variable  quantities,  and,  as  the 
speed  of  the  eoiler  calender  rolls  are  sometimes  changed  to  suit 
different  conditions  of  draft  and  weight  of  sliver,  we  may  also 
consider  the  ratio  as  being  a  variable  quantity.  Now  considering 


C4  COTTON   MILL   MACHINERY   CALCULATIONS. 

these  three  points   as  varying  quantities,  the  following   gives   a 
production  constant :  • 

2X3.1416X600X50X.95 

==  .1421. 

36X7,000 

This  constant  will  apply  only  on  the  later  type  of  Whitin 
combers,  with  a  loss  of  time  of  5  per  cent,  based  on  10  hours  a 
day.  The  production  can  be  figured  from  the  above  constant  by 
the  following  rule: 

Production  constant  x  nips  per  minute  x  ratio  x  grains  per 
yard  in  sliver  =  pounds  per  day. 

Example:  What  would  be  the  production  of  a  Whitin 
comber  at  120  nips  per  minute,  delivering  a  50  grain  sliver,  allow- 
ing for  5  per  cent  loss  of  time?  Ratio  between  cylinder  speed 
and  coiler  roll  speed  is  1.2. 

.1421  X  120  X  1.2  X  50  =  102.31  pounds. 

This  figure  corresponds  closely  with  the  production  figured 
above.  When  there  is  little  or  no  chance  of  the  ratio  between  the 
coiler  rolls  and  the  cylinder  shaft  being  changed,  a  constant  can 
be  worked  out  considering  only  the  nips  per  minute  and  the 
weight  of  the  sliver  as  being  variable  quantities.  With  gears  as 
used  this  constant  would  be  .17052,  and  this  constant  multiplied 
by  the  weight  of  sliver  and  the  nips  per  minute  would  give  the 
production  in  pounds,  as  follows: 

.17052X120X50  =  102.312  pounds  produced. 

The  production  on  the  Mason  comber  can  be  found  by  the 
same  method  as  used  above.  The  ratio  between  the  speed  of  the 
cylinder  and  the  coiler  calender  rolls  is  found  by  the  following : 

1X53X21X24 

=  1.03. 

90X16X18 

The  difference  in  the  two  ratios  on  the  two  machines  can  be 
explained  by  the  difference  in  the  amount  of  draft  in  the  draw- 
box.  The  greater  the  draft  at  this  point,  the  larger  the  ratio  has 
to  .be. 

Example:  Find  the  production  on  a  Mason  comber  at  100 
nips  per  minute,  60  grain  sliver,  10  hours  a  day  and  5  per  cent, 
loss  of  time.  The  1  11/16  inch  coiler  rolls  are  5.3  inches  in 
circumference. 

100  X  1.03  X  5.3  X  600  X  60  X  .95 

—  =  74  Ibs.  produced 
36X7,000 


COMBING.  65 

As  there  is  practically  no  change  in  tension  between  the 
coiler  rolls  and  the  draw-box,  the  above  ratio  of  1.03  will  remain 
the  same  and  a  production  constant  can  be  worked  out,  consider- 
ing only  the  speed  of  the  machine  and  the  weight  of  the  sliver 
as  being  variables,  as  follows : 

1.03X5.3X600X.95 

—  =  .123. 
36X7,000 

Multiplying  this  production  constant  by  the  nips  per  minute 
and  the  weight  of  sliver  will  give  the  production. 

The  speed  of  the  driving  pulleys  on  the  combers  is  simply  a 
matter  of  taking  the  nips  per  minute  and  multiplying  by  the  ratio 
between  the  cylinder  shaft  and  the  driving  shaft.  "  On  the  Whitin 
frame  2.66  revolutions  of  driving  shaft  are  necessary  to  get 
one  revolution  of  cylinder  shaft  and  with  the  machine  running 
at  120  nips  per  minute,  the  driving  pulleys  would  make  2.66  x  120 
=  319  revolutions  per  minute.  The  calculation  for  the  size  of 
pulley  needed  to  drive  the  machine  is  similar  to  that  used  before. 


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RAILWAYS  A  ND    DRAWING.  69 

CHAPTER  V. 


RAILWAY  HEADS  AND  DRAWING  FRAMES — DRAFT,  SPEED,  AND 
PRODUCTION  CALCULATIONS — METALLIC  AND  LEATHER  ROLLS 
— PRODUCTION  CONSTANTS. 

RAILWAY  HEADS. 

The  essential  difference  between  the  railway  head  and  the 
drawing  frame  is  the  fact  that  the  railway  attempts  to  overcome 
the  irregularities  in  the  card  sliver  by  a  change  in  the  speed  of  the 
rolls,  while  the  drawing  frame  has  no  such  mechanism;  and  its 
evening  effect  is  obtained  solely  from  the  fact  that  there  are  six 
ends  doubled  at  the  back,  drawn  out  and  delivered  as  one  end  at 
the  front,  of  about  the  same  weight  as  the  single  ends  received 
at  the  back.  In  the  old  style  of  railway  head,  connected  direct  to 
a  line  of  cards  by  means  of  a  travelling  apron,  or  trough,  it  was 
essential  that  the  front  roll  be  the  one  to  vary  in  speed  as  the 
material  increased  in  weight  but,  after  the  introduction  of  the  mod- 
ern revolving  flat  card,  the  railways  took  their  slivers  from  cans 
and  the  back  rolls  on  some  were  the  ones  that  were  made  to  vary 
in  speed  according  to  the  bulk  of  material  passing  through  the 
evener  trumpet  on  the  front. 

In  Fig.  25  is  shown  a  diagram  of  the  gearing  of  the  railway 
head  built  by  the  Lowell  Machine  Shop.  It  will  be  noticed  that 
the  front  roll  is  driven  from  the  top  cone,  which  is  driven  from 
the  bottom  cone,  and  hence  the  top  cone  speed  varies  with  the 
position  of  the  cone  belt,  this  latter  depending  upon  the  pull 
exerted  by  the  sliver  as  it  passes  through  the  evener  trumpet, 
thus  giving  a  corresponding  variation  in  the  speed  of  the  front 
i  oil.  The  back  roll  is  driven  at  a  constant  speed  from  the  driving 
shaft,  and  the  second  and  third  rolls  are  driven  from  the  back  roll. 
The  draft  gear  is  located  on  the  end  of  the  top  cone  shaft.  The 
break  draft  occurs  between  the  front  and  second  drawing  rolls, 
and  this  draft  changes  with  any  movement  of  the  cone  belt  or 
with  any  change  in  the  size  of  the  draft  gear,  the  drafts  be- 
tween the  other  rolls  remaining  the  same.  This  is  in  accordance 
with  the  old  custom  of  using  the  railway  in  connection  with  the 
old  style  stationary  flat  cards. 

Considering  we  are  using  common  rolls,  or  steel  fluted  bottom 
rolls  with  leather  covered  top  rolls,  the  following  gives  the  draft 
constant  between  the  front  and  back  rolls,  both  diameters  being 
expressed  as  eighths : 


70 


COTTON   MILL   MACHINERY   CALCULATIONS. 


12XXX72X30X60 

—  =  .15   draft  constant. 
36X32X37X27X9 

Rule  for  using:  draft  constant: 
Constant  x  gear  =  draft. 
Draft  -7-  constant  =  gear. 

Then  a  draft  gear  of  40  teeth  would  give  a  total  draft  of  6, 
as  follows: 

.15  X  40  =  6. 

It  is  assumed  and  understood  that  the  evener  cone  belt  is 
working  midway  of  the  cones,  where  the  diameters  of  the  two  are 


FIG.  25.    GEARING  PLAN  OF  LOWELL  RAILWAY  HEAD. 


the  same  and  they  do  not  affect  the  draft.  In  runnning  railways 
this  point  should  be  looked  after,  as  it  gives  plenty  of  leeway  for 
belt  movement  in  either  direction  when  variations  in  weight  of 
card  sliver  occur. 

In  Fig.  26  is  shown  a  diagram  of  the  gearing  of  the  railway 
head  built  by  the  Whitin  Machine  Works.  In  general  plan  it  is 
similar  to  the  one  just  illustrated.  Using  leather  rolls  the  follow- 
ing gives  the  draft  constant,  figuring  between  the  2 1/2  inch  calen- 
der and  the  V/-\  inch  back  drawing  rolls,  both  diameters  being  ex- 
pressed as  eighths : 


20XXX44X55 
43X30X24X9 


=  .1738  draft  constant. 


RAILWAYS  AND  DRAWING. 


71 


Then  a  draft  gear  of  30  teeth  will  give  a  draft  of :  30  x  .1738 
=  5.214. 

In  Fig.  27  is  shown  a  diagram  of  the  gearing  of  the  railway 
head  built  by  the  Saco-Pettee  Co.  Some  differences  will  be 
noticed  in  the  construction  as  compared  with  the  two  just  consid- 
ered. The  front  roll  is  driven  by  a  belt  from  the  driving  shaft 
under  the  frame,  and  has  a  constant  speed.  The  front  roll  drives 
the  second  roll.  The  back  roll  is  driven  from  the  front  roll  by 
means  of  two  short  cones  and  a  friction  belt,  and  has  a  variable 


FIG.  26.    GEARING  PLAN  OF  WHITIN  RAILWAY  HEAD. 

speed  depending  upon  the  position  of  the  cone  belt.  The  back  roll 
drives  the  third  roll.  Any  change  in  speed  of  back  roll,  due  to 
change  in  size  of  draft  gear  or  movement  of  cone  belt,  will  change 
the  draft  between  the  second  -and  third  rolls,  the  other  drafts  re- 
maining the  same. 


72 


COTTON   MILL  MACHINERY   CALCULATIONS. 


Figuring  between  the  2  inch  calender  and  the  IVs  inch  back 
drawing  roll,  we  get  the  following  draft  constant : 

16X32X24X100X60 

=  292  draft  constant. 

24X45X26XXX9 

Rule  for  using  draft  constant  on  Saco-Pettee  railway  head: 

Constant  -r-  draft  =  gear. 

Constant  -7-  gear  =  draft. 

Therefore  a  50  tooth  draft  gear  will  give  a  draft  of  5.84. 


FIG.  27.    GEARING  PLAN  OF  SACO-PETTEE  RAILWAY  HEAD. 


DRAWING  FRAMES. 

Fig.  28  shows  a  diagram  of  the  gearing  of  the  drawing  frame 
built  by  the  Lowell  Machine  Shop.  This  gearing  is  different  from 
those  to  follow  in  that  the  draft  gear  is  located  in  the  position 
ordinarily  occupied  by  the  crown  gear,  a  larger  draft  gear  having 
the  effect  of  causing  a  slower  speed  of  the  back  roll,  hence  in- 
creasing, instead  of  decreasing,  the  draft;  and  also  the  third  roll 
drives  the  back  roll  instead  of  the  back  roll  driving  the  third  roll, 
as  is  the  common  practice.  The  gears  on  the  end  of  back  and 
calender  rolls  are  numbered  two  sizes,  the  letter  c  referring  to  the 


RAILWAYS  AND  DRAWING. 


73 


size  gear  to  use  with  common  rolls  and  the  letter  ra  for  metallic 
rolls. 

Using  the  gearing  for  common  rolls  and  figuring  between 


FIG.  28.    GEARING  PLAN  OF  LOWELL  DRAWING  FRAME. 


calender  and  back  drawing  rolls,  using  a  41  tooth  draft  gear,  we 
get  a  total  draft  of  6.46,  as  follows: 

24X61X22X41X65X28X27 

=  6.46  total  draft. 

45X61X26X25X25X25X  9 

By  leaving  out  the  draft  gear  of  41  teeth  in  the  above  calcu- 
lation, we  get  the  draft  constant,  as  lollows : 

24X61X22XXX65X28X27 

=  .1576  draft  constant. 

45X61X26X25X25X25X  9   ' 

Rule  for  using  draft  constant  on  Lowell  drawing  frame: 
Constant  x  gear  =  draft. 
Draft  -T-  constant  =  gear. 

By  using  the  same  method  of  figuring  we  can  get  the  follow- 
ing intermediate  drafts: 

Draft  occurring  between  first  and  second  drawing  rolls : 

11X35X45 

—  =  3.08  draft. 
25X25X9 

Draft  occurring  between  second  and  third  drawing  rolls: 

9  X25X25X41X65 


1.626  draft. 


45X35X26X25X  9 

Draft  occurring  between  third  and  back  drawing  rolls: 


COTTON   MILL  MACHINERY   CALCULATIONS. 
9X27X28 


=  1.209  draft. 


25X25X  9 

Draft  occurring  between  calender  and  front  drawing  rolls : 

24X61X22 


1.066  draft. 


45X61X11 

The  product  of  these  four  intermediate  drafts  should  be 
equal  to  the  total  draft,  as  figured  previously,  or : 

3r08  X  1.626  X  1.209  X  1.066  =  6.46  total  draft. 

In  using  metallic  rolls  on  either  drawing  frames  or  railways, 
the  common  custom  is  to  use  a  1%  inch  front  roll  and  a  1%  inch 
roll  for  the  other  three  lines,  bottom  and  top  rolls  the  same  size. 
The  rolls  are  made  of  different  pitch,  that  is,  different  number 
of  flutes  for  each  inch  in  diameter;  a,  32  pitch  roll  being  more 
commonly  used  on  the  front  line,  while  a  32  or  24  pitch  roll  is 
used  on  the  second  line,  a  24  pitch  roll  is  used  on  the  third  line 
and  a  16  pitch  roll  is  used  on  the  back  line.  On  account  of  the 
crimping  action  of  the  flutes  the  rolls  deliver  more  than  a  smooth 
roll  of  the  same  diameter.  The  pitch  line  collars,  located  just 
beyond  the  flutes,  keep  the  flutes  from  bottoming,  thus  prevent- 
ing the  cutting  of  the  material  as  it  passes  through  the  rolls.  The 
flutes  of  the  coarser  fluted  rolls  are  deeper  and  cause  a  greater 
crimping  of  the  material  and  give  a  greater  increase  to  the  deliv- 
ery of  the  roll.  The  collars  on  the  24  and  32  pitch  rolls  are  of 
such  size  as  to  give  about  the  same  increase  in  delivery,  tests 
having  been  made  which  indicate  this  increase  at  about  33  per 
cent.  The  16  pitch  roll,  being  coarser  fluted  and  the  flutes  deeper, 
gives  about  47  per  cent,  increase  in  delivery  over  a  common  roll 
of  the  same  diameter.  From  the  above,  we  can  get  the  effective 
diameter  of  any  metallic  roll  by  increasing  its  diameter  by  33  per 
cent,  or  47  per  cent,  depending  upon  its  pitch,  and  this  method 
can  be  used  in  working  out  draft  on  metallic  rolls. 

The  following  table  gives  the  diameters,  the  pitch,  the  effect- 
ive diameters  and  the  effective  diameters  reduced  to  sixths,  so  as 
to  facilitate  the  finding  of  draft,  etc : 

1  inch  roll,  32  pitch,  effective  diameter  1.33,  figured  as  8/6. 

li/8  inch  roll,  32  pitch,  effective  diameter  1.50,  figured  as  9/6. 

1*4  inch  roll,  32  pitch,  effective  diameter  1.66,  figured  as  10/6. 

1%  inch  roll,  32  pitch,  effective  diameter  1.83,  figured  as  11/6. 

li/2  inch  roll,  32  pitch,  effective  diameter  2.00,  figured  as  12/6. 

It  should  be  remembered  that  any  24  pitch  roll  can  be  figured 
as  a  32  pitch  roll. 


RAILWAYS  AND  DRAWING.  75 

1%  inch  roll,  16  pitch,  effective  diameter  1.66,  figured  as  10/6. 

li/4  inch  roll,  16  pitch,  effective  diameter  1.83,  figured  as  11/6. 

1%  inch  roll,  16  pitch,  effective  diameter  2.00,  figured  as  12/6. 

iy2  inch  roll,  16  pitch,  effective  diameter  2 J  7,  figured  as  13/6. 

A  2  inch  calender  roll  is  figured  as  12/6. 

A  21/2  inch  calender  roll  is  figured  as  15/6. 

A  3  inch  calender  roll  is  figured  as  18/6. 

With  the  above  table  as  reference,  it  is  easy  to  figure  the 
draft  of  metallic  rolls.  The  pitch  of  a  metallic  roll  is  easily 
detected  by  the  appearance  of  the  flutes  but,  if  not  certain,  count 
the  number  of  flutes  and  divide  by  the  diameter  of  the  roll. 

In  Fig.  29  is  shown  a  diagram  of  the  gearing  of  the  drawing 
frame  built  by  the  Whitin  Machine  Works,  geared  for  metallic 
rolls.  The  total  draft  between  the  3  inch  calender  roll  and  the 
IVs  inch,  16  pitch  back  drawing  roll,  using  a  30  tooth  draft  gear, 
is  as  follows: 

18X55X19X72X70 

—  =  6.27   total   draft. 
30X56X30X30X10 

^The  diameters  of  the  calender  and  back  rolls  are  expressed 
as  18  and  10  as  shown  in  the  table  above. 

By  leaving  out  the  draft  gear  of  30  teeth  in  the  above  calcu- 
lation, we  get  the  draft  constant. 

18X55X19X72X70 

—  =  188  draft  constant. 
30X56X30XXX10 

Rule: 

Constant  ~-  gear  =  draft. 

Constant  -t-  draft  =  gear. 

Assuming  the  front  and  second  rolls  to  be  32  pitch,  the  third 
roll  24  pitch  and  the  back  roll  16  pitch,  we  can  figure  the  draft 
between  the  different  rolls,  as  follows : 

Draft  between  calender  and  front  rolls : 

18X55X19 

-=1.017  draft. 

30X56X11 

Draft  between  front  and  second  rolls : 

11X40X30 

=  2.716  draft. 


20X27X  9 

Draft  between  second  and  third  rolls : 

9X27X20X72X70X27X24 


30X40X30X30X26  X36X 


=  1.74   draft. 


7C 


COTTON  MILL  MACHINERY   CALCULATIONS. 

Draft  between  third  and  back  rolls: 

9  X36X26 


=  1.30  draft. 


24X27X10 

The  product  of  these  four  intermediate  drafts  is  6.25,  which 
is  very  close  to  that  figured  direct  from  the  gearing. 


FIG.  29.    GEARING  PLAN  OF  WHITIN  DRAWING  FRAME. 


The  actual  drafts  on  the  railways  or  the  drawing  frames, 
as  figured  from  the  weight  of  the  slivers  on  back  afid  front,  vary 
somewhat  from  the  figured  drafts  as  obtained  from  the  gearing. 
This  difference  is  due  to  the  varying  amount  of  crimping  of  the 
material  by  the  flutes  of  the  rolls,  and  the  amount  of  such  varia- 
tion depends  upon  the  bulk  of  the  material  being  handled.  For 
instance,  with  the  same  drafts  and  speed,  a  heavy  sliver  being 
doubled  and  fed  into  the  back  of  the  machine,  will  show  less  varia- 
tion in  the  actual  and  figured  drafts  than  if  a  light  sliver  was 
being  handled.  This  is  explained  by  the  fact  that  the  heavy  mass 
of  fibers  entering  the  back  rolls  do  not  yield  to  the  crimping  action 
of  the  flutes  to  the  extent  that  a  lighter  mass  of  fibers  would,  and 
hence  the  increase  in  the  working  diameter  of  the  back  roll  is  not 
so  great.  When  the  mass  has  reached  the  front  rolls,  its  bulk  has 
been  decreased  enough  to  allow  of  the  full  crimping  effect  of  these 
rolls.  However,  draft  calculated  by  the  above  method  will  come 
near  enough  to  the  actual  draft  for  most  practical  purposes. 

Fig.  30  shows  a  diagram  of  the  gearing  of  the  drawing  frame 


RAILWAYS  AND   DRAWING. 


77 


built  by  the  Saco-Pettee  Co.  The  following  gives  the  draft 
constant,  with  common  rolls,  figuring  between  the  2  inch  calender 
and  the  1%  inch  back  rolls: 

16X32X24X100X60 

—  =  316  draft  constant. 
24X45X24XXX9 

Figuring  the  draft  constant  for  metallic  rolls,    we    get   the 
I'ollowing : 


12X42X24X100X60 


=  280  draft  constant. 


24X45X24XXX10 

Using  a  45  tooth  draft  gear  with  metallic  rolls  will  give  only 
a  draft  of  6.22,  while  with  common  rolls  the  same  gear  will  give 


>  ® 


FIG.  30.    GEARING  PLAN  OF  SACO-PETTEE  DRAWING  FRAME. 

a  draft  of  7.02.  This  readily  shows  the  increase  in  the  crimping 
of  the  coarse  fluted  back  rolls  over  the  finer  fluted  front  rolls,  for 
if  both  the  front  and  back  rolls  crimped  the  material  to  the  same 
extent,  the  drafts  with  metallic  and  leather  rolls  would  be  the 
same. 


78  COTTON  MILL  MACHINERY   CALCULATIONS. 

A  diagram  of  the  gearing  of  the  drawing  frame  built  by 
Howard  &  Bullough,  American  Machine  Co.  is  shown  in  Fig.  31. 
Figuring  for  metallic  rolls  between  the  3  inch  calender  and  the 
11/8  inch  back  roll,  we  get  the  following  draft  constant : 


FIG.  31.    GEARING  PLAN  OF  HOWARD  &  BULLOUGH  DRAWING 
FRAME. 


RAILWAYS  AND  DRAWING. 


79 


18X108X19X98X66 
52  X  62  X22XXX10 


336.8   draft  constant. 


A  diagram  of  the  gearing  of  the  drawing  frame  built  by  the 
Mason  Machine  Works  is  shown  in  Fig.  32.  This  gearing  is 
arranged  for  metallic  rolls.  The  draft  constant  is  311,  as  shown 
below : 

15X31X90X48 

=  311  draft  constant. 

44X22XXX10 

Rule  for  using  the  above  two  constants : 
Constant  -f-  draft  =  gear. 
Constant  -f-  gear  =  draft. 


FIG.  32.    GEARING  PLAN  OF  MASON  DRAWING  FRAME. 


From  the  foregoing  it  will  be  seen  that,  with  the  exception  of 
the  Lowell  drawing  frame,  all  the  frames  are  geared  very  simil- 
arly. In  each  case  a  larger  draft  gear  will  drive  the  back  roll 
faster,  feed  in  more  material,  decrease  the  draft  and  increase 
the  weight  of  the  sliver  on  the  front.  The  Saco-Pettee  railway 
is  similarly  arranged,  while  the  Lowell  and  Whitin  railways  are 
differently  constructed.  A  larger  draft  gear  on  these  last  two  has 
the  effect  of  increasing  the  speed  of  the  front  roll,  increasing  the 
draft  and  reducing  the  weight  of  the  sliver. 

The  following  rule  will  give  the  actual  draft  of  the  frames : 


80  COTTON  MILL   MACHINERY   CALCULATIONS. 

Weight  of  single  sliver  on  back  x  doublings. 

=  draft. 

Weight  of  sliver  on  front. 

The  draft  increases  as  the  size  of  the  draft  gear  decreases 
and  the  following  holds  good  on  all  except  the  Whitin  railway  and 
the  Lowell  railway  and  drawing : 

Gear  on  the  frame  x  draft  of  the  frame 

_ =  draft  gear  needed 

Draft  desired 

Example:  If  a  drawing  frame  with  a  50  tooth  draft  gear 
has  a  draft  of  6,  what  size  gear  will  be  needed  to  give  a  draft 
of  5.75? 

50X6 

—  =  52  tooth  draft  gear. 

5.75 

On  the  Lowell  railway  and  drawing  and  the  Whitin  railway 
the  rule  would  be  as  follows : 

Gear  on  frame  x  draft  desired 

=  draft  gear  needed. 

Draft  of  the  frame 

In  dealing  with  the  weight  of  the  sliver  and  the  draft  gear, 
the  following  rule  applies,  with  the  same  exceptions  as  noted 
above,  and  enables  a  change  of  draft  gear  direct  to  give  any  desir- 
ed variation  in  weight  of  sliver : 

Gear  on  frame  x  weight  of  sliver  desired 

=  draft  gear 

Weight  of  sliver  on  frame  needed. 

Example :  If  a  drawing  frame  is  producing  a  50  grain  sliver 
with  a  60  tooth  draft  gear,  what  size  draft  gear  will  be  needed 
if  the  sliver  is  desired  to  be  42  grains  in  weight? 

60X42 

— 1=  50.4  or  50  tooth  draft  gear  needed. 
50 

On  the  Lowell  railway  and  drawing  and  the  Whitin  railway 
the  above  rule  would  be  changed  to  read  as  follows : 

Gear  on  frame  x  weight  of  sliver  on  frame 

1 =  draft    gear 

Weight  of  sliver  desired.  needed. 

PRODUCTION. 

The  basis  of  the  production  calculations  on  the  above  frames 
is  the  speed  of  the  front  roll  and  the  weight  of  the  sliver.  In  deal- 
ing with  the  older  types  of  railways  and  those  geared  as  shown  in 


RAILWAYS  AND  DRAWING.  81 

Figs.  25  and  26,  the  speed  of  the  front  roll  is  a  variable  quantity, 
depending  upon  the  size  of  the  draft  gear  and  the  position  occupied 
by  the  cone  belt.  Consequently  there  is  always  present  a  chance 
for  error.  On  the  drawing  frames  and  those  railways  that  have 
a  constant  front  roll  speed,  the  production  can  be  figured  accu- 
rately. There  is  always  present  a  small  element  of  error  in  the 
calculations  due  to  the  fact  that  there  is  a  greater  length  of 
sliver  delivered  to  the  can  than  is  delivered  by  the  front  roll,  due 
to  the  tension  between  thes-e  points,  necessary  to  keep  the  ends 
tight.  However,  this  is  small  and  may  be  neglected. 

Example:  What  is  the  production  in  a  ten  hour  day  of  a 
drawing  frame,  if  the  front  roll  is  1%  inches  in  diameter,  making 
400  revolutions  per  minute  and  delivering  a  50  grain  sliver? 
Allow  for  20  per  cent,  loss  of  time  and  assume  the  use  of  common 
rolls.  The  circumference  of  a  1%  inch  common  roll  is  4.32  inches, 
then: 

4.32X400X600X50X.80 

=  164.6  pounds  produced. 

36X7,000 

By  eliminating  the  two  variable  quantities,  the  speed  of  the 
front  roll  and  the  weight  of  the  sliver,  we  get  the  production  con- 
stant, as  follows : 

4.32X600X.80 

=  .00823-.      ' 

36X7,000 

Rule  for  using  the  production  constant : 

Production  constant  x  revolutions  per  minute  of  front  roll 
x  weight  of  sliver  =  pounds  per  day  production. 

Example:  Find  the  production  of  a  drawing  frame  with  a 
front  roll  speed  of  400  revolutions  per  minute  and  delivering  a 
50  grain  sliver? 

.00823  X  400  X  50  =  164.6  pounds. 

The  above  constant  applies  to  all  railways  or  drawing  frames 
with  1%  inch  front  common  roll,  based  on  a  ten  hour  day,  with 
20  per  cent  loss  of  time  for  stoppages. 

In  dealing  with  frames  equipped  with  metallic  rolls,  we  must 
allow  for  the  extra  delivery  of  the  front  roll  due  to  the  crimping 
action  of  the  flutes.  This  crimping,  as  has  been  noted  in  a  32 
pitch  roll,  amounts  to  about  33  per  cent.,  so,  in  the  above  calcula- 
tion, we  can  increase  the  circumference  of  the  front  roll  by  33  per 
cent.,  and  in  place  of  the  4.32  inches  used,  put  5.75  inches  as  the 
circumference  of  the  metallic  roll.  This  will  give  a  calculated  pro- 
duction of  219  pounds  instead  of  164.6.  Another  method  of  get- 


82  COTTON   MILL   MACHINERY    CALCULATIONS. 

ting  the  same  thing  would  be  to  increase  the  production  figured 
for  common  rolls  by  33  per  cent. 

The  above  production  constant  of  .00823  can  be  increased  by 
33  per  cent.,  which  will  give  a  production  constant  that  can  be 
used  for  metallic  rolls,  as  follows :  .00823  x  1.33  =  .01095  produc- 
tion constant  for  metallic  rolls.  The  same  rule  for  use  of  this 
constant  applies  as  before,  then:  .01095  x  400  x  50  =  219  pounds 
produced. 

In  the  above,  one  delivery  is  assumed  as  the  basis.  The  pro- 
duction of  a  drawing  frame  varies  directly  with  the  speed  of  the 
front  rolls  and  the  weight  of  the  sliver. 

Example:  A  drawing  frame  is  producing  160  pounds  per 
day  with  a  front  roll  speed  of  400.  What  speed  would  be  required 
to  give  a  production  of  140  pounds  per  day? 

400X140 

—  =  350  revolutions  per  minute  of  front  roll. 
160 

Example:  A  drawing  frame  is  delivering  a  50  grain  sliver 
and  producing  160  pounds  per  day.  What  would  be  the  production 
if  the  weight  of  the  sliver  was  increased  to  56  grains? 

160X56 

—  =  179.2  pounds. 
50 

ROLL  SETTING. 

No  fixed  rule  can  be  given  for  getting  the  distance  to  set  the 
rolls  of  a  drawing  frame  or  railway  head.  As  a  general  state* 
ment,  the  lighter  the  bulk  of  material  handled  and  the  higher 
the  speed  of  the  rolls,  the  closer  they  can  be  set.  The  following 
distances  are  usually  given  as  good  usage,  based  on  stock  1  inch 
long : 

Between  front  and  second  rolls,  l^i". 
Between  second  and  third  rolls,  l1/^"- 
Between  third  and  back  rolls,  !3/4". 

The  above  figures  apply  to  leather  rolls  and,  in  using  metallic 
rolls,  they  will  have  to  be  increased  by  about  Vs"  in  each  case. 
They  w'll  not  hold  good  in  all  cases,  as  experience  will  show.  The 
only  real  test  of  the  correctness  of  the  settings  is  in  the  appear- 
ance of  the  sliver  as  it  leaves  the  front  rolls.  Irregular  and  un- 
even drawing  will  show  up  at  this  point  and  will  be  easily  detected. 


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84  COTTON  MILL  MACHINERY   CALCULATIONS. 

CHAPTER  VI. 


HANKS  AND  NUMBERS. 

The  machines  following  the  drawing  frames  are  called  fly 
frames  or  roving  frames.  This  is  simply  a  continuation  of  the 
drawing  process,  but  with  the  idea  of  gradually  reducing  the  bulk 
of  the  material  to  a  suitable  size  and  putting  it  in  a  convenient 
form  to  be  used  on  the  spinning  frames.  Three  processes  of  fly 
frames  are  usually  used,  though,  in  coarse  work,  the  general  rule 
is  two  processes,  or  sometimes  only  one,  while  in  making  fine 
yarns  four  processes  are  used.  The  machines  are  called  the 
slubber,  the  intermediate,  the  fine  frame  and  the  jack  frame,  each 
having  the  same  end  in  view  and  being  built  to  handle  material 
of  gradually  decreasing  bulk.  In  the  mills  the  fine  frames  are 
spoken  of  as  speeders  and  the  names  coarse  speeder  and  fine 
speeder  are  often  used  to  designate  the  intermediate  and  fine 
frames. 

Up  to  this  point  we  have  dealt  with  the  weight  of  the  product 
of  the  different  machines,  expressed  as  ounces  or  grains  per  yard  ; 
but,  when  we  reach  the  fly  frames,  the  product  is  referred  to  as 
roving  and  we  no  longer  use  its  weight  to  designate  its  size,  but 
use  a  different  system,  the  size  of  the  roving  being  designated  by 
the  hank  and  spoken  of  as  a  certain  size  hank  roving,  as  four 
hank  roving.  So,  before  taking  up  the  calculations  on  the  fly 
frames,  it  is  best  to  give  a  review  of  this  system,  together  with 
some  rules  and  examples  that  will  be  needed  when  working  with 
hanks. 

The  principles  underlying  the  numbering  of  roving  or  yarn 
are  the  same,  and  are  based  on  two  fundamental  facts: 

First.     That  840  yards  always  constitute  a  hank. 

Second.  That  840  yards,  or  one  hank,  of  one  hank  roving  or 
number  one  yarn,  always  weighs  7,000  grains  or  one  pound. 

Then  the  hank  or  size  of  any  roving,  or  the  number  or  -counts 
of  any  yarn,  corresponds  to  the  number  of  hanks  of  that  yarn  or 
roving  that  it  takes  to  weigh  one  pound,  or  7,000  grains. 

If  we  measure  off  840  yards  of  roving  and  find  that  it  weighs 
one  pound,  it  would  be  called  one  hank  roving,  or  1  H.  R.,  and 
one  yard  of  it  weighs  8.33  grains,  as :  7,000  -=-  840  =  8.33. 

If  we  measure  off  840  yards  of  roving  and  find  that  it  weighs 
one-half  pound  or  3,500  grains,  it  would  be  called  2  H.  R.,  because 
it  takes  two  hanks  of  it  to  weigh  one  pound  and  one  yard  of  it 
weighs  4.166  grains,  as :  3,500  ~  840  =  4.166. 

When  we  speak  of  10  H.  R.  we  mean  that  it  takes  10  hanks 


HANKS  AND  NUMBERS.  85 

of  it,  or  10  X  840  =  8,400  yards,  to  weigh  one  pound.  Then  it  will 
be  seen  that  the  hank  of  the  roving  or  the  counts  of  the  yarn  refer 
to  the  number  of  hanks  that  it  will  take  to  weigh  one  pound. 

By  dividing  7,000  grains  by  the  weight  in  grains  of  one  hank, 
or  840  yards,  of  any  roving  or  yarn,  we  get  the  hank  or  counts 
of  that  roving  or  yarn.  As  it  is  not  necessary  or  convenient  to 
measure  off  840  yards  when  sizing  our  roving  or  yarn,  it  is  cus- 
tomary to  reel  only  12  yards  of  roving  and  divide  its  weight  in 
grains  into  100  and  to  reel  120  yards  of  yarn  and  divide  its  weight 
in  grains  into  1000,  as  12  and  120  bear  the  same  ratio  to  100  and 
1,000  as  840  does  to  7,000. 

Example:  If  f!2  yards  of  roving  weigh  25  grains,  what  is 
its  size  or  hank? 

100  -s-25  =  4  H.  R. 

Example :  If  120  yards  of  yarn  weigh  40  grains,  what  is  its 
size  or  counts  ? 

1,000  -^  40  =  25's  yarn. 

In  dealing  with  odd  lengths  of  yarn  or  roving,  the  following 
rule  will  be  found  useful,  and  is  the  basis  of  several  others : 

The  number  of  yards  of  roving  or  yarn  x  8-33  ~-  weight  in 
grains  of  the  length  taken  —  the  size. 

Example:  If  20  yards  of  roving  weigh  33  grains,  what  is 
its  size? 

20X8.33 

—  —  5  H.  R. 
33 

One  thing  must  be  borne  in  mind  when  dealing  with  hanks 
and  counts :  The  larger  the  H.  R.,  the  less  it  weighs  per  yard  and 
the  greater  the  number  of  yards  or  hanks  it  takes  to  weigh  one 
pound;  the  smaller  the  H.  R.,  the  greater  the  weight  per  yard 
and  the  less  the  number  of  yards  or  hanks  it  takes  to  weigh  one 
pound.  For  instance,  a  2  H.  R.  weighs  4.166  grains  per  yard  and 
there  are  1,680  yards  or  2  hanks  to  one  pound,  while  a  6  H.  R. 
weighs  1.388  grains  per  yard  and  there  are  5040  yards  or  6  hanks 
to  one  pound. 

The  weight  per  yard  of  any  roving  can  be  found  by  dividing 
8.33  by  the  hank  of  the  roving,  and  the  weight  of  12  yards  can 
be  found  by  dividing  100  by  the  hank  of  the  roving. 

The  following  rules  and  examples  will  be  found  useful  in 
figuring  drafts  and  numbers  on  the  fly  frames.  In  figuring  on 
the  slubber,  the  material  on  the  back  is  expressed  by  the  weight 
per  yard  and  this  must  be  reduced  to  hanks,  by  dividing  this 


Sb  COTTON   MILL  MACHINERY   CALCULATIONS. 

weight  into  8.33,  to  correspond  with  the  roving  on  the  front,  or 
the  weight  of  the  roving  on  the  front  can  be  figured  in  grains  per 
yard  and  this  weight  reduced  to  its  equivalent  hank  roving. 

Example :  If  the  sliver  on  the  back  of  the  slubber  weighs  60 
grains  per  yard  and  the  draft  of  the  machine  is  4,  what  is  the  H.  R. 
delivered  on  the  front? 

60  -f-  4  =  15  grains.     8.33  H-  15  =  .55  H.  R. 

In  this  case  the  weight  on  the  back  of  the  slubber  is  divided 
by  the  draft,  which  gives  15  grains  per  yard  as  the  weight  of  the 
roving.  Then  8.33  divided  by  this  weight  will  reduce  it  to  its 
equivalent  hank. 

From  the  hank  roving  on  the  front  of  the  slubber  and  the 
draft,  it  is  easy  to  figure  the  weight  of  the  sliver  on  the  back  by 
the  following  rule: 

Divide  the  H.  R.  on  front  of  slubber  by  the  draft  and  divide 
8.33  by  this  number. 

Example:  A  slubber  has  a  draft  of  4  and  is  running  a  .55 
H.  R.  What  is  the  weight  of  the  drawing  sliver  on  the  back? 

.55  -r-  4  =  .1375.     8.33  -*-  .1375  —  60  grains. 

In  working  with  the  weight  of  the  material  on  the  previous 
machines,  the  weight  on  the  back  divided  by  the  draft  gave  the 
weight  on  the  front,  but,  in  dealing  with  hanks,  the  weight  de- 
creasing as  the  number  increases,  the  reverse  is  true  and  the  hank 
on  the  back,  multiplied  by  the  draft,  will  give  the  hank  on  the 
front.  On  the -intermediate  and  fine  frames,  where  there  are  two 
ends  doubled  in  the  creel  to  be  drawn  and  combined  into  one  end 
on  the  front,  the  size  of  the  single  roving  in  the  creel  must  be 
divided  by  two.  For  illustration,  two  ends  of  2  H.  R.  doubled  in 
the  creel  are  the  equivalent  in  size  and  weight  of  one  end  of  1  H.  R. 
and  should  be  so  treated;  also  5  H.  R.  doubled  in  the  creel  is  the 
equivalent  of  a  single  2.5  H.  R. 

From  the  above  we  get  the  following  rules.  Rule  to  find  the 
H.  R.  a  frame  is  delivering  when  the  draft  and  H.  R.  in  the  creel 
are  known: 

H.  R.  in  creel  *  draft  -=-  2  =  H.  R.  on  front. 

Example:  The  H.  R.  in  creel  is  1.5  doubled,  draft  of  ma- 
chine is  5,  what  is  the  H.  R.  on  the  front? 

1.6X6 

—  =  3.75  H.  R.  on  front. 
2 

Rule  to  find  the  draft  when  the  H.  R.  on  front  and  in  the  creel 
are  known : 


HANKS  AND  NUMBERS.  87 

H.  R.  on  front  X  2  ~  H.  R.  in  creel  =  draft. 
Example:     The  H.  R.  being  delivered  on  front  is  15,     with 
5  H.  R.  doubled  in  the  creel.    What  is  the  draft? 

15X2 

—  =6  draft. 

5 

Rule  to  find  the  H.  R.  in  the  creel,  the  draft  of  the  machine 
and  the  H.  R.  on  front  being  known : 

H-  R.  on  front  x  2  -=-  draft  =  H.  R.  in  the  creel. 

Example :  If  the  H.  R.  on  the  front  is  10  and  the  draft  is  5, 
what  is  the  size  of  the  single  roving  in  the  creel? 

10X2 

=  4  H.  R.  in  the  creel. 

5 

The  following  problem,  worked  out  first  by  the  hanks  and  sec- 
ondly, by  the  weight  of  the  material,  will  illustrate  clearly  both 
methods  and  serve  to  show  that  either  one  is  correct. 

Example:  What  size  roving  is  being  made  if  the  sliver  on 
the  back  of  the  slubber  weighs  42  grains  per  yard?  The  slubber 
has  a  draft  of  4,  the  intermediate  a  draft  of  5,  and  the  fine  frame 
a  draft  of  6,  with  roving  doubled  in  the  creels  of  the  intermediate 
and  fine  frames. 


(1).      8.33  -f-  42  =  .198. 
.198X4X5X6 


=  5.95  H.  R. 


2X2 
(2).       42X2X2 


=  1.4. 


4X5X6 

8.33  -f-  1.4  =  5.95  H.   R. 

In  working  the  above  example,  the  first  method  was  to  re- 
duce the  42  grain  sliver,  on  the  back  of  the  slubber,  to  .198  hank 
sliver  by  dividing  8.33  by  42  and  then  multiplying  this  .198  by  the 
drafts  on  the  three  fly  frames  and  dividing  by  the  doublings  on  the 
intermediate  and  fine  frames.  In  the  second  method  illustrated, 
the  weight  of  the  sliver  on  the  back  of  the  slubber  was  divided 
by  the  drafts  of  the  three  frames  and  multiplied  by  the  doublings 
on  the  intermediate  and  fine  frames.  This  gives  the  weight,  in 
grains  per  yard,  of  the  fine  roving,  and  8.33  divided  by  this  weight 
irives  the  size  of  the  roving. 


8X 


COTTON  MILL   MACHINERY   CALCULATIONS. 

TABLE    FOR    NUMBERING    ROVING. 


12yds 
grains 

Hank 
roving. 

12yds 
weigh 
grains 

Hank 

roving. 

12yds 
weigh 
grains 

Hank 
roving 

12yds 
weigh 
grains 

Hank 

roving. 

12  vds 
weigh 
grains 

Hank 

roving. 

1. 

100.00 

9. 

11.11 

16. 

6.25 

83. 

4.35 

30. 

3.33 

.2 

83.33 

.1 

10.99 

.1 

6.21 

.1 

4.33 

.1 

3.32 

.4 

71.43 

.2 

10.87 

6.17 

.2 

4.31 

.2 

3.31 

.6 

62.50 

.3 

10.75 

'.3 

6.13 

.3 

4.29 

.3 

3.30 

.8 

55.56 

.4 

10.64 

.4 

6.10 

.4 

4.27 

.4 

3.29 

3. 

50.00 

.5 

10.53 

.5 

6.06 

4.26 

.5 

3.28 

.2 

45.45 

.6 

10.42 

,6 

6.02 

!e 

4,24 

.6 

3.27 

.4 

41.67 

.7 

10.31 

.7 

5.99 

.7 

4.22 

.7 

3.26 

.6 

38.46 

.8 

10.20 

.8 

5.95 

.8 

4.20 

.8 

3.25 

.8 

35.71 

.9 

10.10 

.9 

5.92 

.9 

4.18 

.9 

3.24 

3. 

33.33 

10 

10.00 

17. 

5.88 

34. 

4.17 

31 

3.23 

.1 

32.26 

.1 

9.90 

.1 

5.85 

.1 

4.15 

.1 

3.22 

.2 

31.25 

.2 

9.80 

.2 

5.81 

4.13 

.2 

3.21 

.3 

30.30 

.3 

9.71 

.3 

5.78 

'.3 

4.12 

.3 

3.19 

.4 

29.41 

.4 

9.62 

.4 

5.75 

A 

4.10 

.4 

3.18 

.5 

28.57 

.5 

9.52 

.5 

5.71 

4.08 

.5 

3.17 

.6 

27.78 

.6 

9.43 

.6 

5.68 

'A 

4.07 

.6 

3.16 

.7 

27.03 

.7 

9.35 

.7 

5.65 

i 

4.05 

.7 

3.15 

.8 

20.32 

.8 

9.26 

.8 

5.62 

.8 

4.03 

.8 

3.14 

.9 

25.64 

.9 

9.17 

.9 

5.59 

.9 

4.02 

.9 

3.13 

4. 

25.00 

11. 

9.09 

18. 

5.56 

35. 

4.00 

32. 

3.12 

.1 

24.39 

.1 

9.01 

.1 

5.52 

.1 

3.98 

.1 

3.12 

.2 

23.81 

.2 

8.93 

.2 

5.49 

.2 

3.97 

.2 

3.11 

.3 

23.26 

.3 

8.85 

.3 

5.46 

.3 

3.95 

.3 

3.10 

.4 

22.73 

.4 

8.77 

.4 

5.43 

.4 

3.94 

.4 

3.09 

.5 

22.22 

.5 

8.70 

.5 

5.41 

.5 

3.92 

.5 

3.08 

.6 

21.74 

.6 

8.62 

.6 

5.38 

.6 

3.91 

.6 

3.07 

.7 

21.28 

.7 

8.55 

.7 

5.35 

.7 

3.89 

..7 

3.06 

.8 

20.83 

.8 

8.47 

.8 

5.32 

.8 

3.88 

.8 

3.05 

.9 

20.41 

.9 

8.40 

.9 

5.29 

.9 

3.86 

.9 

3.04 

5. 

20.00 

13. 

8.33 

19. 

5.26 

36. 

3.85 

33. 

3.03 

.1 

19.61 

.1 

8.26 

.1 

5.24 

.1 

3.83 

.1 

3.02 

.2 

19.23 

.2 

8.20 

.2 

5.21 

.2 

3.82 

.2 

3.01 

.3 

18.87 

.3 

8.13 

.3 

5.18 

.3 

3.80 

.3 

3.00 

.4 

18.52 

.4 

8.06 

.4 

5.15 

.4 

3.79 

.4 

2.99 

.5 

18.18 

.5 

8.00 

.5 

5.13 

.5 

3.77 

.5 

2.99 

.6 

17.86 

.6 

7.94 

.6 

5.10 

.6 

3.76 

.6 

2.98 

.7 

17.54 

.7 

7.87 

.7 

5.08 

.7 

3.75 

.7 

2.97 

.8 

17.24 

.8 

7.81 

.8 

5.05 

.8 

3.73 

.8 

2.96 

.9 

16.95 

.9 

7.75 

.9 

5.03 

.9 

3.72 

.9 

2.95 

6. 

16.67 

13. 

7.69 

30. 

5.00 

87. 

3.70 

34. 

2.94 

.1 

16.39 

.1 

7.63 

.1 

4.98 

.1 

3.69 

.1 

2.93 

.2 

16.13 

.2 

7.58 

.2 

4.95 

.2 

3.68 

.2 

2.92 

.3 

15.87 

.3 

7.52 

.3 

4.93 

.3 

3.66 

.3 

2.92 

.4 

15.62 

.4 

7.46 

.4 

4.90 

.4 

3.65 

.4 

2.91 

.5 

15.38 

.5 

7.41 

.5 

4.88 

.5 

3.64 

.5 

2.90 

.6 

15.15 

.6 

7.35 

.6 

4.85 

.6 

3.62 

.6 

2.89 

.7 

14.93 

.7 

7.30 

.7 

.4.83 

.7 

3.61 

.7 

2.88 

.8 

14.71 

.8 

7.25 

.8 

4.81 

.8 

3.60 

.8 

2.87 

.9 

14.49 

.9 

7.19 

.9 

4.78 

.9 

3.58 

.9 

2.87 

7. 

14.29 

14. 

7.14 

21 

4.76 

38. 

3.57 

35. 

2.86 

.1 

14.08 

.1 

7.09 

.1 

4.74 

.1 

3.56 

.1 

2.85 

.2 

13.89 

.2 

7.04 

.2 

4.72 

.2 

3.55 

.2 

2.84 

.3 

13.70 

.3 

6.99 

.3 

4.69 

.3 

3.53 

.3 

2.83 

.4 

13.51 

.4 

6.94 

.4 

4.67 

.4 

3.52 

.4 

2.82 

.5 

13.33 

.5 

6.90 

.5 

4.65 

.5 

3.51 

.5 

2.82 

.G 

13.16 

.6 

6.85 

.6 

4.63 

.6 

3.50 

.6 

2.81 

.7 

12.99 

.7 

6.80 

.7 

4.61 

^ 

3.49 

.7 

2.80 

.8 

12.82 

.8 

6.76 

.8 

4.59 

'.» 

3.47 

.8 

2.79 

.9 

12.66 

.9 

6.71 

.9 

4.57 

.9 

3.46 

.9 

2.79 

8. 

12.50 

15. 

6.67 

33. 

4.55 

39. 

3.45 

36. 

2.78 

.1 

12.35 

.1 

6.62 

.1 

4.52 

.1 

3.44 

.1 

2.77 

.2 

12.20 

.2 

6.58 

.2 

4.50 

.2 

3.42 

.2 

2.76 

.3 

12.05 

.3 

6.54 

.3 

4.48 

,3 

3.41 

.3 

2.75 

.4 

11.90 

.4 

6.49 

.4 

4.46 

.4 

3.40 

.4 

2.75 

.5 

11.76 

.5 

6.45 

.5 

4.44 

.5 

3.39 

.5 

2.74 

.6 

11.63 

.6 

fi.41 

.6 

4.42 

.6 

3.38 

.6 

2.73 

.7 

11.49 

.7 

6.37 

.7 

4.41 

.7 

3.37 

.7 

2.72 

.8 

11.36 

.8 

6.33 

.8 

4.39 

.8 

3.36 

.8 

2.72 

.9 

11.24 

.9 

6.29 

.9 

4.37 

.9 

3.34 

.9 

2.71 

HANKS  AND  NUMBERS. 
TABLE   FOR    NUMBERING   ROVING. 


12yds. 
weigh 
•grains. 

Hank 

roving. 

12  vds. 
wefch 
grains. 

Hank 
roving. 

12yds. 

weigl 
grains. 

Hank 

roving. 

12  yds. 
weigh 
grains. 

Hank 
roving. 

12yds. 
weigh 
grains. 

Hank 
roving 

37. 

2.70 

48. 

2.08 

65 

1.54 

100 

1.00 

190 

.53 

.1 

2.70 

.2 

2.07 

.5 

1.53 

101 

.99 

192 

.52 

.2 

2.69 

.4 

2.07 

66. 

1.52 

102 

.98 

194 

.52 

.3 

2.68 

.6 

2.06 

1.50 

103 

.97 

196 

.51 

.4 

2.67 

.8 

2.05 

67'° 

1.49 

104 

.96 

198 

.51 

.6 

2.67 

49 

2.04 

.5 

1.48 

105 

.95 

•-•'in 

.50 

.6 

2.66 

.2 

2.03 

68. 

1.47 

106 

.94 

202 

.50 

.1 

2.65 

.4 

2.02 

.5 

1.46 

107 

.93 

204 

.49 

.8 

2.65 

.6 

2.02 

69. 

1.45 

108. 

.93 

206 

.49 

.9 

2.64 

.8 

2.01 

1.44 

109 

.92  • 

208 

.48 

38. 

2.63 

50. 

2.00 

70! 

1.43 

110 

.91 

210 

.48 

.1 

2.62 

.2 

1.99 

.5 

1.42 

111 

.90 

212 

.47 

.2 

2.62 

.4 

1.98 

71. 

1.41 

112 

.89 

214 

.47 

.3 

2.61 

.6 

1.98 

.5 

1.40 

113 

.88 

216 

.46 

.4 

2.60 

.8 

1.97 

72. 

1.39 

114 

.88 

218 

.46 

.5 

2.60 

51. 

1.96 

1.38 

115 

.87 

220 

.45 

.6 

2.59 

.2 

1.95 

73!° 

1.37 

116 

.86 

222 

.45 

.7 

2.58 

.4 

1.95 

.5 

1.36 

117 

.85 

224 

.45 

.8 

2.58 

.6 

1.94 

74. 

1.35 

118 

.85 

226 

.44 

.9 

2.57 

.8 

1.93 

1.34 

119 

.84 

228 

.44 

39. 

2.56 

52. 

1.92 

75! 

1.33 

130 

.83 

230 

.43 

.1 

2.56 

.2 

1.92 

.5 

1.32 

121 

.83 

235 

.43 

.2 

2.55 

.4 

1.91 

76. 

1.32 

122 

.82 

240 

.42 

.3 

2.54 

.6 

1.90 

.5 

1.31 

123 

.81 

245 

.41 

.4 

2.54 

.8 

1.89 

77. 

1.30 

124 

.81 

250 

.40 

.0 

2.53 

53 

1.89 

.5 

1.29 

125 

.80 

255 

.39 

.0 

2.53 

.2 

1.88 

78. 

1.28 

126 

.79 

260 

.38 

.7 

2.52 

.4 

1.87 

.5 

1.27 

127 

.79 

265 

.38 

.8 

2.51 

.6 

1.87 

79. 

1.27 

128 

.78 

270 

.37 

.9 

2.51 

.8 

1.86 

.5 

1.26 

129 

,78 

275 

.36 

40. 

2.50 

54. 

1.85 

80. 

1.25 

130 

.77 

280 

.36 

.2 

2.4'J 

.2 

1.85 

.5 

1.24 

131 

.76 

285 

.35 

.4 

2.48 

.4 

1.84 

81. 

1.23 

132 

.76 

290 

.34 

.6 

2.40 

.6 

1.83 

.5 

1.23 

133 

.75 

295 

.34 

.8 

2.45 

.8 

1.82 

82. 

1.22 

134 

.75 

300 

.33 

41. 

2.44 

55. 

1.82 

.5 

1.21 

135 

.74 

305 

.33 

.2 

2.43 

.2 

1.81 

83. 

1.20 

136 

.74 

SW 

.32 

.4 

2.42 

.4 

1.81 

.5 

1.20 

137 

.73 

315 

.32 

.6 

2.40 

.6 

1.80 

84. 

1.19 

138 

.72 

320 

.31 

.8 

2.39 

.8 

1.79 

.5 

1.18 

139 

.72 

330 

.30 

42. 

2.38 

56. 

1.79 

85. 

1.18 

140 

.71 

340 

.29 

.2 

2.37 

.2 

1.78 

1.17 

141 

.71 

350 

.29 

.4 

2.30 

.4 

1.77 

86.5 

1.16 

142 

.70 

300 

.28 

.6 

2.35 

.6 

1.77 

.5 

1.16 

143 

.70 

370 

.27 

.8 

2.34 

.8 

1.76 

87. 

1.15 

144 

.69 

880 

.26 

43. 

2.33 

57. 

1.75 

.5 

1.14 

145 

.69 

390 

.26 

.2 

2.31 

.2 

1.75 

88. 

1.14 

146 

.68 

400 

.25 

.4 

2.30 

.4 

1.74 

.5 

1.13 

147 

.68 

410 

.24 

.6 

2.29 

.6 

1.74 

89. 

1.12 

148 

.68 

420 

.24 

.8 

2.28 

.8 

1.73 

.5 

1.12 

149 

.67 

430 

.23 

44. 

2.27 

58. 

1.72 

9O. 

1.11 

150 

.67 

440 

.23 

.2 

2.2G 

.2 

1.72 

.5 

1.10 

152 

.66 

450 

.22 

.4 

2.25 

.4 

1.71 

91. 

1.10 

154 

.65 

460 

.22 

.6 

2.24 

.6 

1.71 

.5 

1.09 

156 

.64 

470 

.21 

.8 

2.23 

.8 

1.70 

92. 

1.09 

158 

.63 

480 

.21 

45. 

2.22 

59. 

1.69 

.5 

1.08 

160 

.02 

490 

.20 

.2 

2.21 

.2 

1.69 

93. 

1.08 

162 

.02 

500 

.20 

.4 

2.20 

.4 

1.68 

.5 

1.07 

164 

.01 

525 

.19 

.6 

2.19 

.6 

1.68 

94. 

1.06 

166 

.00 

550 

.18 

.8 

2.18 

.8 

1.07 

.5 

1.06 

168 

.00 

575 

.17 

46. 

2.17 

6O. 

1.67 

95. 

1.05 

170 

.59 

6OO 

.17 

.2 

2.16 

.5 

1.65 

.5 

1.05 

172 

.58 

625 

.16 

.4 

2.16 

61. 

1.64 

96. 

1.04 

174 

.57 

650 

.15 

.6 

2.15 

.5 

1.63 

.5 

1.04 

176 

.57 

075 

.15 

.8 

2.14 

62. 

1.01 

97. 

1.03 

178 

.56 

700 

.14 

47. 

213 

.5 

1.00 

.5 

1.03 

180 

.56 

725 

.14 

.2 

2.12 

63. 

1.59 

98. 

1.02 

182 

.55 

775 

.13 

.4 

2.11 

.5 

1.57 

.5 

1.02 

184 

.54 

825 

.12 

.6 

2.10 

64. 

1.56 

99. 

1.01 

186 

.54 

900 

.11 

.8 

2.09 

.5 

1.55 

.5 

1.01 

188 

.53 

1000 

.10 

TWIST   OF    ROVING. 


Twist, 

Twist, 

Hank                'Twist' 

Twist, 

Hank 

Square  1.2  X 

"nv    i  Square  1.2  x 

1.2  x 

*rovk  S(luare 

1.2  X 

rov- 

root. 

sq. 

.           root.       sq. 

intr      i     rOOt. 

sq. 

1T1W 

root. 

sq. 

ing. 

root. 

root. 

ing. 

root. 

ing. 

root. 

.10 

.316 

.38 

.80      .894 

1.07 

3.30 

1.483 

1.78 

4.32 

2.078 

2.49 

.11 

.332 

.40 

.82      .906 

1.09 

2.22 

1.490 

1.79 

4.36 

2.088!  2.51 

.12 
.13 
.14 

.346 
.361 
.374 

.41 
.43 
.45 

.84 
.86 

.ss 

.917 
.927 
.938 

1.10 
1.11 
1.13 

2.25 
2.28 
2.31 

1.500 
1.510 
1.520 

1.80 
1.81 
1.82 

4.40 
4.44 
4.48 

2.098 
2.107 
2.117 

m 

2.54 

.15 

.387 

.46 

.90 

.949 

1.14 

2.34 

1.530 

1.84 

4.52 

2.12*' 

2.55 

.16 

.400 

.48 

.92 

.959 

1.15 

2.37 

1.539 

1.85 

4.50 

2.135 

2.50 

.17 

.412 

.49 

.94 

.970 

1.16 

2.40 

1.549 

1.86 

4.60 

2.145 

2.57 

.18 

.424 

.51 

.96 

.980 

1.18 

2.43 

1.559 

3.87 

4.64   2.154 

2.58 

.19 

.436       .52 

.98 

.990 

1.19 

2.46 

1.568 

1.88 

4.08   2.163 

2.00 

.20 

.447        .54 

1.00 

1.000 

1.20 

2.49 

1.578 

1.89 

4.72   2.173 

2.01 

.21 

.458 

55 

1.02 

1.010 

1.21 

2.r,  2 

1.587 

1.90 

4.76 

2.182 

2.152 

.22 

.469 

.56 

1.04 

1.020 

1.22 

2.r,r, 

1.597 

1.92 

4.80 

2.191 

2.03 

.480 
.490 

J58 
.59 

1.06 
1.08 

1.030 
1.039 

1.24 
1.25 

2.58 
2.61 

1.606 
1.616 

1.93 
1.94 

4.84 
4.88 

2.201 
2.209 

2.04 
2.65 

'.2-> 

.500 

.60 

1.10 

1.049 

1.26 

2.64 

1.625 

1.95 

4.92 

2.218 

2.66 

.510 

.61 

1.12 

1.058 

1.27 

2.67 

1.634 

1.90 

4.96 

2.227 

2.67 

.27 

.520 

.62 

1.14 

1.068 

1.28 

2.70 

1.643 

1.97 

5.00 

2.236 

2.68 

!28 

.529 

.63 

1.16 

1.077 

1.29 

2.7:: 

1.652 

1.98 

5.04 

2.245 

2.09 

.29 

.539 

.65 

1.18 

1.086 

1.30 

2.76 

1.661 

1.99 

5.08 

2.254 

2.70 

.30 

.548 

.66 

1.20 

1.095 

1.31 

3.79 

1.670 

2.00 

5.13 

2.263 

2.72 

.31 

.557 

.67 

1.22 

1.105 

1.33 

2.S2 

1.679 

2.01 

5.16 

2.272 

2.73 

.32 

.566 

.68 

1.24 

1.114 

1.34 

2.85 

1.688 

2.03 

5.20 

2.280 

2.74 

.33 

.574 

.69 

1.26 

1.122 

1.35 

2.8S 

1.697 

2.04 

5.24 

2.281 

2.75 

.34 

.583 

.70 

1.28 

1.131 

1.36 

2.91 

1.706 

2.05 

5.28 

2.298 

2.7(5 

.35 

.592 

.71 

1.30 

1.140 

1.37 

2.94 

1.715 

2.06 

5.32 

2.307 

2.77 

.36 

.600 

.72 

1.32 

1.149 

1.38 

1.723 

2.07 

5.36 

2.315 

2.78 

.37 

.608 

.73 

1.34 

1.158 

1.39 

r>  oo 

1.732 

2.08 

5.40 

2.324 

2.79 

.38 

.616 

.74 

i.:;.; 

1.166 

1.40 

3.03 

1.741 

2.09 

5.44 

2.332 

2.80 

.39 

.624 

.75 

1.38 

1.175 

1.41 

3.06 

1.749 

2.10 

5.48 

2.341 

2.81 

.40 

.632 

.  .76 

1.4O 

1.183 

1.42 

3.09 

1.758 

2.11 

.•>.r»2 

2.349 

2.82 

.41 

.640 

.77 

1.42 

1.1D2 

1.43 

1.766 

2.12 

.V.56 

2.358 

2.83 

.42 

.648 

.78 

1.44 

1.200 

1.44 

::!i5 

1.775 

2.13 

5.60 

2.366 

2.84 

.43 

.656 

.79 

1.4(5 

1.208 

1.45 

3.18 

1.783 

2.14 

5.64 

2.375 

2.85 

.44 

.(563 

.80 

1.48 

1.217 

1.46 

3.21 

1.792 

2.15 

5.68 

2.383 

2.86 

.45 

.671 

.80 

1.50 

1  .225 

1.47 

3.24 

1.800 

2.16 

5.72 

2.::;  12 

2.87 

.46 

.678 

.81 

1.52 

1.233 

1.48 

3.27 

1.808 

2.17 

5.76 

2.400 

2.88 

.47 

.686 

.82 

1.54 

1.241 

1.49 

3.30 

1.817 

2.18 

5.80 

2.408 

2.89 

.48 

.693 

.83 

1.50 

1.249 

1.50 

3.33 

1.825 

2.19 

5.84 

2.416 

2.90 

.49 

700 

.84 

1.58 

1.257 

1.51 

3.36 

1.833 

2.20 

5.88 

2.42.-, 

2.91 

.50 

.707 

.85 

1.6O 

1.205 

3.39    1.841 

2.21 

5.92 

2.433 

2.92 

.51 

.714 

.86 

1.02 

1.273 

1.53 

3.42    1.849 

2.22 

5.96 

2.441 

2.93 

.52 

.721 

.87 

1.64 

1.281 

1.54 

3.4.,    1.857 

2.23 

6.00 

2.449 

2.94 

.53 

.728 

.87 

1.66 

1.288 

1.55 

3.48    1.865 

2.24 

0.04 

2.458 

2.95 

.54 

.735 

.88 

1.08 

1.290 

1.56 

3.51 

1.873 

2.25 

(5.08 

2.46,6 

2.93 

.55 

.742 

.89 

1.70 

1.304 

1.56 

1.881 

2.2(5 

0.12 

2.474 

2.1.7 

.56 

.748 

.90 

1.72 

1.311 

1.57 

X57 

1.889 

2.27 

6.16 

2.482 

2.98 

.57 

.755 

.91 

1.74 

1.319 

1  .58 

3.00 

1.897 

2.28 

0.20 

2.41)0 

2.99 

.58 

.762 

.91 

1.70 

1.327 

1.59 

3.63 

1.905 

2.29 

6.24 

2.41)8 

3.00 

.59 

.768 

.92 

1.78 

1  .334 

1.60 

3.66 

1.913 

2.30 

0.28 

2..-.06 

3.01 

.60 

.775 

.93 

1.80 

1.342 

1.61 

3.69 

1.921 

2.31 

6.32 

2.514 

3.02 

.61 
.62 
.63 

.781 
.787 
.794 

.94 
.94 
.95 

1.82 
1.84 
1.86 

1.349 
1.356 
1.364 

1.62 
1.63 
1.64 

3.72 
3.7.'> 
3.78 

1.929 
1.936 
1.944 

L.31 
2.32 
2.33 

oi'ld 
6.44 

2.522   3.03 
2.530   3.04 
2.5381  3.05 

.64 

.800 

.96 

1.88 

1.371 

1.65 

3.81 

1.952 

2.34 

0.48 

2.546 

3.05 

.65 

.806 

.97 

1.90 

1.378 

1.05 

3.84 

1.960 

2.35 

6.52 

2.553 

3.06 

.66 

.812 

.97 

1.1)2 

1.386 

1.66 

3.87 

1.967 

2.36 

6.56 

2.561 

3.07 

.67 

.819 

.98 

1.94 

1.393 

1.07 

3.90 

1.975 

2.37 

6.60 

2.56!) 

3.08 

.68 

.825 

.99 

1.96 

1.400 

1.68 

3.93 

1.982 

2.38 

6.64 

2.577 

3.09 

.69 

.831 

1.00 

1.98 

1.407 

1.69 

3.90 

1.990 

2.39 

6.68 

2.r>  S5 

3.10 

.70 

.837 

i.oo 

2.00 

1.414 

1.70 

3.99 

1.997 

2.40 

6.72  2.592 

3.11 

.71 

.843 

1.01 

2.02 

1.421 

1.71 

4.02 

2.005 

2.41 

0.7(5 

2.000 

3.12 

.72 

.849 

1.02 

2.04 

1.428 

1.71 

4.05 

2.012 

2.41 

6.80 

2.608 

3.13 

.73 

.854 

1.02 

2.00 

1.435 

1.72 

4.08 

2.020 

2.42 

6.84 

2.615 

3.14 

.74 

.860 

1.03 

2.'  IS 

1.442 

1.73 

4.11 

2.027 

2.43 

6..  8  8 

2.023 

3.1  5 

.75 
.76 

.866 
.872 

1.04 
1.05 

2.10 
2.12 

1.449 

1.456 

1.74 
1.75 

4.14 
4.17 

2.035 
2.042 

2.44 
2.45 

(5.D2 
6.1)6 

2.031 
2.638 

3.16 
3.17 

.77 

.877     1.05 

2.14 

1.463 

1.76 

4.20 

2.049 

2.46 

7.00 

2.646 

3.17 

.78 
.79 

.883  j  1.O6 
.889     1.07 

2.10    1.470 
2.18   1.476 

1.76 
1.77 

4.23 
4.26 

2.067  2.47 

2.064J  2.48 

7.04 
7.08 

2.653 
2.661 

3.18 
3.19 

TWIST   OF   ROVING. 


Hank 
rov- 
ing. 

Square 
root. 

'Twirt 
1.2  x 
sq. 
root. 

Hank 

rov- 
ing. 

Square 
root. 

sq. 
root. 

Hank 

Square 
root. 

Twist 
1.2  X 
sq. 
root. 

Hank 
rov- 
ing. 

Square 
root. 

Twist, 
1.2  X 
sq. 
root. 

7.10 

2.665 

3.20 

10.62 

3.259 

3.91 

14.84 

3.852 

4.62 

19.76 

4.445 

5.33 

7.15 

2.674 

3.21 

10.68 

3.208 

3.92 

14.91 

3.861 

4.63 

19.84 

4.454 

5.35 

7.20 

2.683 

10.74 

3.277 

14.98 

3.870 

4.64 

19.92 

4.463 

5.36 

7.25 

2J593 

:$;23 

10.80 

3.28(5 

3/l't 

15.05 

3.879 

4.00 

20  00 

4.472 

5.37 

7.30 

2.702 

3.24 

10.8(5 

3.295 

8.96 

15.12 

3.888 

4.07 

20.08 

4.481 

5.38 

7.35 

2.711 

3.25 

10.92 

3.305 

3.97 

15.19 

3.897 

4.08 

2O.10 

4.490 

5.39 

7.40 

2.720 

3.26 

10.98 

3.314 

3.98 

15.2(5 

3.906 

4.09 

20.24 

4.499 

5.40 

7.45 

2.72',) 

3.28 

1  1  .04 

3.323 

3.99 

15.33 

3.915 

4.70 

20.32 

4.508 

5.41 

7.5O 

2.739 

3.29 

11.10 

3.332 

4.00 

15.40 

3.924 

4.71 

2O.4O 

4.517 

5.42 

7.55 

2.748 

3.30 

11.16 

3.341 

4.01 

15.47 

3.933 

4.72 

20.48 

4.525 

5  43 

7.60 

2.757 

11.22 

3.350 

4.02 

15.54 

3.942 

4.73 

20.56 

4.534 

5.44 

7.65 

2.76(5 

::!•!•_• 

11.28 

3.  3  59 

4.03 

15.61 

3.951 

4.74 

20.04 

4.543 

5.45 

7.70 

2.775 

3.33 

11.34 

3.367 

4.04 

15.08 

3.960 

4.75 

20.72 

4.552 

5.46 

7.75 

2.784 

3.34 

11.40 

3.370 

4.05 

15.75 

,",.969 

4.70 

20.80 

4.561 

5.47 

7.80 

2.793 

3.35 

11.46 

3.385 

4.06 

i.-.isL' 

3.977 

4.77 

20.88 

4.569 

5.48 

7.85 

2.8U2 

3.3(5 

11.52 

3.394 

4.07 

15.89 

3.9,8(5 

4.78 

20.90 

4.578 

5.49 

7.90 

2.811 

3.37 

11.58 

3.403 

4.08 

15.96 

3.995 

4.79 

21.04 

4.587 

5.50 

7.95 

2.820 

3.38 

11.64 

3.412 

4.09 

10.03 

4.004 

4.80 

21.12 

4.596 

5.51 

8.00 

2.SL-S 

3.39 

11.70 

3.421 

4.10 

16.10 

4.012 

4.81 

21.2O 

4.604 

5.52 

8.05 

2.837 

3.40 

11.7(5 

3.429 

4.12 

10.17 

4.021 

4.83 

21.28 

4.613 

5.54 

8.10 

2.84(5 

3.42 

11.82 

3.438 

4.13 

10.24 

4.030 

4.84 

21.30 

4.622 

5.55 

8.15 

2.85  5 

3.43 

11.88 

3.447 

4.14 

10.31 

4.039 

4.85 

21.44 

4.630 

5.56 

8.20 

2.864 

3.44 

11.94 

3.455 

4.15 

10.38 

4.047 

4.86 

21.52 

4.639 

5.57 

8.25 

2.872 

3.45 

12.00 

3.4(54 

4.16 

10.45 

4.056 

4.87 

21.00 

4.648 

5.58 

8.30 

2.881 

3.46 

12.06 

3.473 

4.17 

10.52 

4.064 

4.88 

21.68 

4>>56 

5.59 

8.35 

2.890 

3.47 

12.12 

3.481 

4.18 

10.59 

4.073 

4.89 

21.70 

4.005 

5.60 

8.40 

2.898 

3.48 

12.18 

3.490 

4.19 

10.00 

4.082 

4.90 

21.84 

4.073 

5.61 

8.45 

2.907 

3.49 

12.24 

3.499 

4.20 

10.73 

4.090 

4.91 

21.92 

4.682 

5.62 

8.5O 

2.915 

3.50 

12.3O 

3.507 

4.21 

16.80 

4.099 

4.92 

22.OO 

4.690 

5.63 

8.55 

2.924 

3.51 

12.36 

3.516 

4.22 

16.87 

4.107 

4.93 

22.08 

4.699 

5.64 

8.60 

2.933 

12.42 

3.524 

4.23 

16.94 

4.116 

4.94 

22.10 

4.707 

5.65 

8.65 

2.941 

3ir>3 

12.48 

3.533 

4.24 

17.01 

4.124 

4.95 

22.24 

4.716 

5.66 

8.70 

2.950 

3.54 

12.54 

3.541 

4.25 

17.08 

4.133 

4.90 

22.32 

4.724 

5.67 

8.75 

2.95,8 

3.55 

12.60 

3.550 

4.26 

17.15 

4.141 

4.97 

22.40 

4.733    5.68 

8.80 

2.96(5 

3.50 

12.00 

3.558 

4.27 

17.22 

4.150 

4:98 

22.48 

4.741    5.69 

8.85 

2.975 

.",.57 

12.72 

3.5(57 

4.28 

17.29 

4.158 

4.99 

22.56 

4.750 

5.70 

8.90 

2.983 

3.58 

12.78 

3.575 

4.29 

17.36 

4.167 

5.00 

22.154 

4.758 

5.71 

8.95 

2.992 

3.59 

12.84 

3.583 

4.30 

17.43 

4.175 

5.01 

22.72 

4.767 

5.72 

9.00 

3.000 

3.60 

13.9O 

3.592 

4.31 

17.50 

4.183 

5.02 

23.80 

4.775 

5.73 

9.05 

3.008 

3.01 

12.90 

3.600 

4.32 

17.57 

4.192 

5.03 

22.88 

4.783 

5.74 

9.10 

3.017 

3.02 

13.02 

.-5.608 

4.33 

17.64 

4.200 

5.04 

22.90 

4.792 

5.76 

9.15 

3-03 

13.08 

3.1517 

4.34 

17.71 

4.208 

5.05 

23.04 

4.800 

5.76 

9.20 

3.033 

3.04 

13.14 

3.625 

4.35 

17.78 

4.216 

5.00 

23.12 

4.808 

5.77 

9.25 

3.041 

3.05 

13.20 

3.633 

4.36 

17.85 

4.225 

5.07 

23.20 

4.817 

5.78 

9.30 

3.60 

13.2:5 

3.641 

4.37 

17.92 

4.233 

5.08 

23.28 

4.825 

5.79 

9.35 

b!()58 

3.67 

18.32 

3.  650 

4.38 

17.99 

4.241 

5.09 

23.36 

4.833 

5.80 

9.40 

3.060 

3.68 

13.38 

3.658 

4.39 

18.06 

4.250 

5.10 

23.44 

4.841 

5.81 

9.45 

3.074 

3.09 

13.44 

3.666 

4.40 

18.13 

4.258 

5.11 

2I5.52 

4.850 

5.82 

9.50 

3.082 

3.70 

13.5O 

3.674 

4.41 

18.20 

4.266 

5.12 

23.60 

4.858 

5.83 

9.55 

3.090 

3.71 

13.5(5 

3.082 

4.42 

18.27 

4.274 

5.13 

23.158 

4.86(5 

5.84 

9.60 

3.098    3-72 

13.62 

•5.691 

4.43 

18.34 

4.283 

5.14 

23.70 

4.874 

5.86 

9.65 

3.100 

3.73 

13.08 

3.699 

4.44 

18.41 

4.291 

5.15 

23.84 

4.883 

5.86 

9.70 

3.114 

3-74 

13.74 

3.707 

4.45 

18.48 

4.299 

5.10 

23.92 

4.891 

5.87 

9.75 

3.122 

3.75 

13.80 

3.715 

4.46 

18.55 

4.307 

5.17 

24.00 

4.899 

5.88 

9.80 

3.130 

3.70 

13.80 

5.723 

4.47 

18.152 

4.315 

5.18 

24.08 

4.907 

5.89 

9.85 

3.138 

3.77 

13.92 

3.731 

4.48 

18.69 

5.19 

24.10 

4.915 

5.90 

9.90 

3.146 

3.78 

13.98 

3.739 

4.49 

18.76 

41331 

5.20 

24.24 

4.923 

5.91 

9.95 

3.154 

3.79 

14.04 

3.747 

4.50 

18.83 

4.339 

5.21 

24.32 

4.932 

5.92 

10.00 

3.102 

3.79 

14.10 

5.755 

4.51 

18.90 

4.347 

5.22 

24.40 

4.940 

5.93 

10.05 

•5.17.0 

3.80 

14.16 

5.763 

4.52 

18.97 

4.355 

5.23 

24.48 

4.948 

5.94 

10.10 

3.178 

3.81 

14.22 

.5.771 

4.53 

19.04 

4.363 

5.24 

24.50 

4.956 

5.95 

10.15 

•5.186 

3.  82 

14.28 

3.779 

4.53 

19.11 

4.371 

5.25 

24.64 

4.964 

5.96 

10.20 

$.194 

'.  \  .  '  >  ',  I 

14.34 

3.787 

4.54 

19.18 

4.379 

5.20 

24.72 

4.972 

5.97 

10.25 

5.202 

3.S  1 

14.40 

3.795 

4.55 

19.25 

4.387 

5.26 

24.80 

4.980 

5.98 

10.30 

5.209 

3.85 

14.46 

3.803 

4.56 

19.32 

4.395 

5.27 

24.88 

4.988 

5.99 

10.35 

3.217 

3.86 

14.52 

3.811 

4.57 

19.39 

4.403 

5.28 

24.96 

4.996 

6.00 

10.40 

3.225 

3.87 

14.58 

3.818 

4.58 

19.46 

4.411 

5.29 

25.04 

5.004   6.00 

10.45 

3.233 

3.88 

14.64 

3.826 

4.59 

19.53 

4.419 

5.30 

25.12 

5.012    6.01 

10.50 
10.55 

3.240 
3.248 

3.89 
3.90 

14.70 
14.76 

3.834 
3.842 

4.60 
4.61 

19.00 
19.67 

4.427 
4.435 

5.31 
5.32 

25.20   5.020    6.02 
25.28    5.028  |  6.03 

COTTON  MILL   MACHINERY   CALCULATIONS. 

CHAPTER  VII. 


FLY    FRAMES — DRAFT — ROLL    SETTINGS — TWIST — DIFFERENTIAL 
OR  COMPOUND — WINDING — CONES — TENSION  AND  LAY  GEAR- 
ING— TAKE-UP  OR  BOTTOM  CONE  GEARING — TAPER  GEARING — 
OR  COMPOUND — WINDING — CONES — TENSION  AND  LAY  GEAR- 
FLY  FRAMES. 

The  object  of  the  fly  frames  is  to  reduce  the  bulky  drawing 
pliver  to  a  suitable  size  and  put  it  into  a  convenient  form  to  be 
used  on  the  spinning  frame,  the  size  of  the  final  roving  and  the 
number  of  frames  used  depending  upon  the  size  and  quality  of 
yarn  desired.  Double  roving  is  used  in  the  creels  for  the  sake  of 
evenness  and  added  strength  to  the  finished  yarn. 

The  action  of  the  fly  frames  can  be  divided  into  three  oper- 
ations, all  three  occurring  at  the  same  time,  viz:  drawing,  twist- 
ing and  winding.  The  drawing  and  twisting  are  comparatively 
simple  operations,  easily  understood  and  necessitating  only  simple 
mechanisms  to  obtain  the  required  results,  while  the  correct  wind- 
ing of  the  roving  on  the  bobbin  is  more  difficult  to  understand, 
requires  more  careful  watching  and  adjusting,  and  calls  for  far 
more  complicated  mechanisms. 

The  drawing  is  accomplished  by  three  lines  of  fluted  steel 
rolls,  suitably  geared,  with  double  bossed  leather  top  rolls,  each 
boss  carrying  one  or  two  rovings.  The  use  of  shell  rolls  on  the 
front  line  and  solid  rolls  on  the  middle  and  back  is  common,  while 
some  use  shell  rolls  on  the  front  and  middle  lines  of  rolls,  or  on 
all  three.  The  best  arrangement  would  be  to  use  the  self -oiling, 
ball-bearing  type  of  shell  rolls  on  all  three  lines  of  rolls.  This 
gives  a  good,  even  smooth  drawing  of  the  fibres,  lessens  the 
chances  of  the  rolls  binding,  and  produces  better  and  smoother 
work  with  less  care  and  attention.  Metallic  rolls  have  been  used 
on  fly  frames  with  success,  but  only  in  a  few  cases- 

The  twisting  is  accomplished  by  the  revolutions  of  the  flyer. 
The  roving  leaves  the  front  roll,  reaches  and  passes  through  the 
nose  of  the  flyer,  goes  down  the  hollow  arm  of  the  flyer  and 
through  the  eye  of  the  presser  foot  onto  the  bobbin.  The  roving, 
by  this  means,  is  practically  held  by  the  flyer,  the  rapid  revolving 
of  which  produces  the  twist.  The  twist  is  introduced  in  the  rov- 
ing between  the  front  roll  and  the  flyer  nose,  the  amount  of  twist 
depending  upon  the  speed  of  the  flyer  and  the  delivery  of  the  front 
roll.  A  faster  front  roll  speed  gives  a  greater  delivery  of  roving 
and  causes  a  corresponding  decrease  in  the  amount  of  twist  put 
in  the  roving. 


FLY  FRAMES.  93 

The  winding  of  the  roving  on  the  bobbin  is  caused  by  the  dif- 
Jterence  in  the  surface  speed  of  the  bobbin  and  the  presser  foot 
of  the  flyer.  The  spindle,  which  carries  the  flyer  and,  conse- 
quently, the  flyer  itself,  is  driven  at  a  constant  speed,  and  the  speed 
of  the  bobbin  is  varied  as  the  bobbin  builds,  so  that,  at  all  stages 
of  its  growth,  the  surface  speed  of  the  bobbin  will  be  equal  to  the 
surface  speed  of  the  presser  foot  plus  the  surface  speed  of  the 
front  roll,  or  its  delivery.  This  necessitates  the  bobbin  to  be 
driven  in  such  a  manner  that  its  speed  can  be  slightly  reduced 
after  the  winding  of  each  layer  of  roving;  being  at  its  fastest 
speed  at  the  start  of  a  set,  when  its  diameter  is  smallest,  and  at 
its  slowest  speed  at  the  finish  of  a  set,  when  its  diameter  is 
largest.  This  is  spoken  of  as  "bobbin  lead,"  the  surface  speed 
of  the  bobbin  always  being  in  excess  of  the  surface  speed  of  the 
presser  foot,  the  bobbin  thus  pulling  the  roving  through  the  flyer 
and  wrapping  it  onto  itself. 

In  the  case  of  the  "flyer  lead"  the  conditions  are  reversed. 
The  bobbin  is  carried  on  the  spindle  and  driven  at  a  constantly  in- 
creasing speed,  while  the  flyer  is  driven  separately  at  a  fixed 
speed,  the  surface  speed  of  the  bobbin  being  always  slower  than 
the  surface  speed  of  the  presser  foot  by  the  amount  of  roving 
delivered  by  the  front  roll.  The  presser  foot,  in  this  case,  wraps 
the  roving  onto  the  bobbin,  which  may  be  said  to  be  lagging  be- 
hind. The  gradually  increasing  speed  of  the  bobbin  is  necessary 
from  the  fact  that,  as  the  bobbin  increases  in  size,  it  takes  less 
wraps  around  it  to  take  up  the  delivery  of  the  front  roll.  Conse- 
quently, as  the  roving  is  wrapped  onto  the  bobbin  by  the  presser 
foot,  the  bobbin  has  to  lag  behind  the  flyer  a  less  number  of  revo- 
lutions. This  method  of  driving  the  bobbins  and  flyers  brought 
about  undesirable  conditions  which  it  is  not  necessary  to  discuss 
here,  but  led  to  the  adoption  of  the  bobbin  lead  type  of  gearing, 
and  all  the  modern  fly  frames  are  built  with  this  feature. 

On  the  modern  fly  frames  the  gradual  reduction  of  the  speed 
of  the  bobbins  is  accomplished  by  driving  the  bobbins  by  means  of 
a  differential  motion  or  "compound,"  the  relative  speed  of  the 
parts  of  the  "compound"  being  controlled  by  the  speed  of  the 
bottom  cone,  the  speed  of  the  bottom  cone  being,  in  turn,  con- 
trolled by  the  position  of  the  cone-belt. 

The  up  and  down  traverse  motion  of  the  bobbin  rail,  the 
length  of  which  is  automatically  decreased  after  each  layer  of 
loving  is  wound,  is  controlled  by  the  builder,  which  also  serves, 
indirectly,  to  shift  the  cone-belt  on  the  cones  and  to  reverse  the 
direction  of  the  rail  at  the  same  time.  The- direct  cause  of  the 
above  motions  is  the  movement  of  the  tumbling  shaft,  which  is 
held  stationary  while  the  builder  dog  or  "flop-over"  is  in  contact 


94  COTTON  MILL  MACHINERY   CALCULATIONS. 

with  the  face  of  the  builder.  This  "flop-over"  is  held  against  the 
face  of  the  builder  by  the  action  of  a  spring  and  lever  acting 
against  a  "dog"  or  cam  on  the  bottom  of  the  tumbling  shaft. 
When  the  traverse  has  reached  the  point  at  which  the  face  of 
the  builder  slides  by  the  "flop-over,"  this  spring  and  lever  move 
the  tumbling  shaft  enough  to  allow  the  gap  gear,  on  its  upper 
end,  to  come  in  contact  with  the  bevel  gear  on  the  end  of  the  top 
cone  shaft.  This  gives  the  tumbling  shaft  a  half  revolution, 
which  moves  the  cone-belt,  through  the  tension  train  of  gearing, 
reverses  the  motion  of  the  rail  by  moving  the  reverse  gear,  and 
shortens  the  traverse  by  closing  the  builder  jaws.  This  closing 
of  the  builder  jaws  is  done  by  the  movement  of  the  cone-belt 
rack ;  thus  the  amount  of  the  shortening  of  the  traverse  depends 
upon  the  movement  of  the  rack,  &nd,  as  this  movement  is  varied 
as  the  size  of  the  roving  varies,  the  finer  the  roving,  the  less 
movement  of  belt  rack  and  the  less  closing  of  the  builder  jaws. 

Fig.  33  shows  a  plan  of  the  general  gearing  of  a  7  inch 
by  3  inch  fly  frame  built  by  the  Woonsocket  Machine  and  Press 
Co.,  Woonsocket,  R.  I.  Figs.  34  and  35  show  the  draft  and  twist 
gearing  on  the  same  frame.  From  these  the  change  gears  men- 
tioned below  can  be  easily  found,  and  also  their  relation  to  the 
other  parts  of  the  frame  can  be  understood. 

There  are,  on  all  fly  frames,  four  things  to  regulate  and 
change  when  making  a  change  in  the  size  of  the  roving  that  is 
being  run : 

First:  The  draft.  This  is  governed  by  the  draft  gear 
which  drives  the  back  roll  and  is  on  the  stud  with  the  crown  gear. 
A  smaller  gear  will  drive  the  back  roll  slower,  feed  in  less 
material,  increase  the  draft,  decrease  the  weight  delivered  by  the 
front  roll  and  give  a  larger  hank  roving. 

Second:  The  twist.  This  is  regulated  by  the  twist  gear 
which  is  on  the  end  of  the  main  or  "compound"  shaft.  This  gear 
drives  the  top  cone  shaft  and,  from  here,  the  front  roll,  thus  con- 
trolling the  speed  and  also  the  delivery  of  the  front  roll.  In  fact 
the  twist  gear  controls,  directly  or  indirectly,  the  speed  of  every 
part  of  the  frame  except  the  spindles,  which  are  driven  from  the 
main  shaft  direct.  A  smaller  twist  gear  drives  the  front  roll 
slower,  decreases  the  delivery  of  the  front  roll,  increases  the  twist 
in  the  roving,  and  would  be  put  on  when  changing  to  a  finer  roving. 

Third :  The  lay  of  the  roving  on  the  bobbin.  This  is  regu- 
lated by  the  lay  or  rail  gear  which  controls  the  speed  of  the  rail, 
thus  producing  the  correct  spacing  of  the  coils  of  roving  on  the 
bobbins.  This  gear  is  located  on  the  end  of  the  reversing  shaft, 
or  at  some  convenient  point  in  the  lay  train  of  gearing.  Not  like 
the  first  two  considered,  there  is  a  lack  of  uniformity  in  the  plac- 


FLY  FRAMES 


COTTON   MILL,  MACHINERY   CALCULATIONS. 


ing  of  this  gear  by  the  different  builders.  A  smaller  gear  drives 
the  rail  slower,  decreases  the  space  allowed  for  each  individual 
coil  of  roving,  and  would  be  called  for  when  changing  to  a  finer 
roving. 

Fourth:  Tension.  This  is  regulated  by  the  tension  or  con- 
tact gear  which  controls  the  distance  the  cone-belt  is  shifted  at 
the  end  of  each  traverse  of  the  rail.  This  shifting  of  the  cone- 
belt  changes  the  speed  of  the  bottom  cone  and  the  "compound" 
and,  consequently,  the  bobbins.  This  gear  is  located  somewhere 
in  the  tension  train  of  gearing  between  the  upright  or  tumbling 
shaft  and  the  cone-belt  rack.  A  smaller  gear  causes  less  move- 
ment to  the  cone-belt  and,  consequently,  a  smaller  decrease  in 


C/POI/V/V 
GEAf? 
/OO' 


TO     I 


/j5j  D/ 


FIG.  34.    DRAFT  GEARING  ON  WOONSOCKET  FLY  FRAMES. 

bobbin  speed,  also  an  increase  in  the  tension  on  the  roving,  and 
would  be  called  for  when  the  roving  is  running  "slack"  or  when 
changing  to  a  finer  roving.  T 

The  four  gears  above  should  be  changed  when  any  decided 
difference  is  made  in  the  size  of  the  roving  run.  A  larger  gear 
in  each  case  above  would  have  the  opposite  effect  noted. 

There  are  two  other  gears  that  may  be  considered  as  change 
gears : 

First:  The  taper  gear.  This  is  a  small  gear  that  regulates 
the  amount  of  closing  of  the  builder  jaws  after  the  winding  of 
each  layer  of  roving  on  the  bobbin,  thus  shortening  the  traverse 
of  the  rail  and  causing  the  taper  on  the  ends  of  the  bobbin.  This 
should  not  be  changed  after  the  correct  taper  on  the  bobbins 
is  once  obtained. 

Second:  The  take-up  or  cone  gear.  On  the  Saco-Pettee  and 
Lowell  frames  this  gear  is  spoken  of  as  the  take-up  gear  and  is 


FLY  FRAMES.  97 

located  on  the  end  of  the  small  shaft,  driven  by  the  bottom  cone, 
which  drives  the  sun- wheel;  while  on  the  Howard  and  Bullough, 
Woonsocket  and  Providence  frames  it  is  spoken  of  as  the  cone 
gear  and  is  located  on  the  end  of  the  bottom  cone.  Under  either 
name  it  serves  the  same  purpose,  viz:  the  regulating  of  the  speed 
of  the  "differential"  or  "compound"  and,  hence,  the  bobbins,  thus, 
together  with  the  starting  position  of  the  cone-belt,  giving  the 
correct  tension  on  the  roving  at  the  start  of  a  set,  or  while  the 
first  layer  of  roving  is  being  wound  on  the  bobbins.  A  smaller 
gear  would  drive  the  "compound,"  also  the  bobbins,  slower,  de- 
creasing the  tension  on  the  roving. 

After  the  proper  gear  is  obtained  and  the  correct  starting 
point  of  the  cone-belt  is  determined,  both  being  dependent  each 
upon  the  other,  there  is  no  need  of  changing  either,  except  in 
case  of  a  change  in  the  diameter  of  the  bobbins  used.  This  would 
call  for  a  change  in  the  tension  at  the  start  and  would  necessitate 
a  readjustment  at  one  or  both  of  the  points  mentioned. 

DRAFT  ON  FLY  FRAMES. 

The  middle  and  back  rolls  are  made  1  inch  in  diameter,  while 
the  front  roll  may  be  1  1/16,  1%,  1  3/16,  or  1*4  inches  in 
diameter.  The  more  common  sizes  are  1^4  inch  front  roll  on 
slubbers  and  the  large  size  intermediates,  and  1%  inch  front  roll 
on  the  small  size  intermediates,  fine  and  jack  frames. 

As  the  weight  of  the  roving  decreases,  the  draft  of  the  rolls 
increases  and,  also,  the  speed  of  the  machine.  Good  average 
drafts  for  the  different  fly  frames  are  as  follows:  Slubbers,  4* 
intermediate,  5;  fine  frame,  6;  and  jack  frame,  7. 

The  use  of  the  larger  drafts  on  the  smaller  frames  is  per- 
missible from  the  fact  that  the  rolls  have  a  smaller  amount  of 
material  to  deal  with.  Consequently  there  is  less  work  on  the  rolls 
and  less  charice  for  slippage  and  poor  drawing. 

The  custom  is  to  use  very  little  draft  between  the  middle 
and  back  rolls,  throwing  most  of  the  draft  between  the  front  and 
middle  rolls.  The  rolls  of  all  fly  frames  are  geared  at  the  head 
end  of  the  machine,  the  arrangement  being  similar  to  the  one 
illustrated  in  Fig.  34,  though  on  extra  long  frames  double  gearing- 
is  resorted  to;  that  is,  the  rolls  are  geared  at  both  ends-  This 
arrangement  overcomes  the  strain  put  on  the  rolls  while  running, 
and  will  have  a  tendency  to  cause  both  ends  of  the  rolls  to  start 
at  the  same  time,  producing  a  smooth,  even  movement  to  the 
rolls.  It  necessitates  the  changing  of  draft  gears  at  both  ends  of 
the  frame,  however. 


98  COTTON   MILL  MACHINERY   CALCULATIONS. 

The  draft  between  the  middle  and  back  rolls  is  found  as 
follows : 

1X25 


1.087  draft. 


23X1 

The  draft  constant  is  found  from  the  following  figures: 

9X100X56 


=  180   draft  constant. 


35X  X  X8 

Constant  -4-  Gear  =  Draft. 
Constant  -£-  Draft  =  Gear. 

The  draft  gearing  varies  with  the  different  makes  of  f ramea 
and  with  frames  of  the  same  make  and  different  sizes,  but  all 
are  arranged  similarly  to  the  one  illustrated. 

The  following  rules  for  changing  the  draft  gear  without  the 
use  of  the  constant  will  be  found  useful.  The  draft  and  hank  rov- 
ing vary  inversely,  and  the  weight  varies  directly  with  the  size  of 
the  gear.  The  larger  the  draft  gear,  the  smaller  the  draft,  the 
smaller  the  hank  roving  and  the  heavier  the  weight  of  the  ma- 
terial delivered. 

In  changing  the  gear  from  the  draft  use  the  "following  rule : 

Gear  on  the  frame  x  draft  on  the  frame  *4-  draft  desired  = 
draft  gear  needed- 

Example :  If  a  frame  is  using  a  30  tooth  draft  gear  and  has 
a  draft  of  6,  what  size  draft  will  be  needed  to  give  a  draft  of  5? 

•  30X6 

—  =  36  draft  gear  needed. 
6  '  • 

By  substituting  hank  roving  in  the  above  rule  in  the  place  of 
draft,  we  can  change  the  draft  gear  for  variations  in  the  size  of 
the  hank  roving. 

Example :  A  frame  is  running  a  6.25  H.  R.  with  a  30  tooth 
draft  gear.  What  size  gear  would  be  needed  to  give  a  5.5  H.  R.? 

30X6.25 

—  =  34  draft  gear  needed. 
5.5 

In  changing  the  draft  gear  by  the  weight  of  the  material 
being  delivered,  the  following  rule  holds  good : 

Draft  gear  on  the  frame  x  weight  desired  H-  weight  on  the 
frame  =  draft  gear  needed. 

Example:  A  frame  running  with  a  30  tooth  draft  gear  is 
delivering  a  roving  that  weighs  17  grains  to  12  yards,  what  size 


FLY  FRAMES.  99 

draft  gear  will  be  needed  to  give  a  weight  of  20  grains  to  12 
yards  ? 

30X20 

—  =  35.3  or  35  tooth  draft  gear  needed. 
17 

In  setting  the  rolls  on  a  fly  frame,  no  fixed  inflexible  rule  can 
be  given,  as  the  distance  between  the  rolls  depends  upon  the 
staple,  the  feel  of  the  fibres,  the  bulk  of  material  being  handled, 
the  draft  and  the  speed  of  the  rolls.  Usually  the  higher  the 
speed  the  larger  the  draft  and  the  finer  the  roving,  and  the  closer 
the  rolls  can  be  set.  A  rule  found  very  good  on  slubbers  and  inter- 
mediates is: 

Distance  between  front  and  middle  rolls,  i/8-inch  greater 
than  the  length  of  the  staple  being  run. 

Distance  between  middle  and  back  rolls,  y^-inch  to  %-inch 
greater  than  the  length  of  the  staple  being  run. 

This  distance  to  be  measured  from  center  to  center  of  rolls. 
On  the  fine  frames  and  in  making  very  fine  roving,  closer  settings 
than  the  above  can  be  used  and  give  better  work.  However,  the 
true  test  of  the  correctness  of  the  setting  of  the  rolls  is  the  ap- 
pearance of  the  roving  as  it  leaves  the  front  roll. 

In  this  connection  it  is  good  to  remember  that  the  best  re- 
sults cannot  be  obtained  unless  the  steel  rolls  are  kept  well  lubri- 
cated at  all  times.  One  of  the  most  satisfactory  lubricants  for 
this  purpose  is  "Non-Fluid  Oil",  as  it  lasts  for  quite  a  while,  is 
easily  applied  and  will  give  excellent  results.  The  same  can  be 
said  in  regard  to  its  use  in  the  bearings  of  drawing,  spinning  and 
twister .  rolls.  These  oils  are  manufactured  by  the  New  York 
and  New  Jersey.  Lubricant  Company  of  New  York. 

TWIST  ON  FLY  FRAMES. 

Each  revolution  of  the  spindle  or  flyer  puts  in  one  turn  of 
twist,  arid  the  amount  of  twist  in  the  roving  depends  upon  the 
ratio  of  the  spindle  speed  and  the  delivery  of  the  front  roll.  If 
the  flyer  made  10  revolutions  while  the  front  roll  was  delivering 
5  inches  of  roving,  each  inch  of  roving  would  contain  2  turns 
or  twists  and  the  twist  in  the  roving  would  be  spoken  of  as  two 
turns.  The  twist  in  roving  is  always  spoken  of  as  so  many  turns 
per  inch. 

Now,  if  we  work  out  the  speed  of  the  spindles  and  the  de- 
livery of  the  front  roll  in  inches,  dividing  the  spindle  speed  by  the 
delivery  of  the  front  roll,  we  find  the  twist,  or  turns  per  inch, 
in  the  roving.  Referring  to  Fig.  35  and  assuming  a  speed  of  400 
R.  P.  M.  of  main  shaft,  we  get  the  following  as  the  speed  of  the 
spindles : 


100 


COTTON  MILL  MACHINERY   CALCULATIONS. 


THS/-S 
G£A*> 

SO-SO        ' — ' 


-rof=>  co /ye:    SHA 


e 


FIG.  35.    TWIST  GEARING  ON  WOONSOCKET  FLY  FRAMES. 


400X45X*3 


=  1*28.5  R.  P.  M. 


30X21 


Assuming  same  speed  to  main  shaft  and  using  a  24  tooth 
gear,  the  following  will  give  the  front  roll  speed : 


400X24X75 
48X128 


=  117.18  R.  P.  M. 


The  front  roll  is  IVs  inches  in  diameter  or  3.534  inches  in 
circumference.  Hence  it  will  deliver  414.11  inches  of  roving  per 
minute.  (117.18  x  3.534  =  414.11).  By  dividing  the  R.  P.  M.  of 
the  spindles  by  this  front  roll  delivery,  we  get  the  twist  as  fol- 
lows: 

1228.5  •*•  414.11  =  2.966  twist  per  inch. 

From  this  it  will  be  clearly  seen  that  the  twist  in  the  roving 
depends  upon  the  ratio  between  the  spindle  speed  and  the  delivery 
of  the  front  roll,  and  any  change  in  this  ratio  will  make  a  corre- 
sponding change  in  the  twist. 

The  usual  method  of  figuring  the  twist  constant,  or  the  twist, 
is  from  the  gearing  direct. 

Start  with  the  circumference  of  the  front  roll  under  the  line, 
put  the  gear  on  the  end  of  the  front  roll  over  the  line,  the  next 
year  under,  the  next  over,  and  continue  alternating  the  gears  till 


FLY  FRAMES.  101 

we  get  to  the  bevel  on  the  bottom  of  the  spindle,  which  will  come 
•under  the  line.  Divide  the  product  of  the  numbers  above  the  line 
by  the  product  of  the  numbers  under  the  line.  The  answer  is 
the  twist. 

The  reason  for  this  will  be  seen  from  the  fact  that,  if  we 
start  with  one  revolution  of  the  front  roll  and  work  out  the 
spindle  speed,  we  will  get  the  revolutions  of  the  spindle  for  each 
revolution  of  the  front  roll,  or  the  number  of  turns  of  twist  that 
is  put  in  the  amount  of  roving  delivered  by  the  one  revolution 
of  the  front  roll.  As  we  want  the  twist  per  inch  and  not  the  twist 
per  revolution  of  front  roll,  we  must  divide  this  by  the  delivery 
of  the  roll  for  one  revolution,  which  is,  of  course,  its  circumfer- 
ence. In  this  case,  the  circumference  of  the  roll  is  3.534  inches, 
and  if  we  start  with  this  figure  under  the  line,  we  get  the  same 
result  as  would  be  gotten  by  the  method  mentioned  above. 

Referring  to  Fig.  35,  using  a  24  tooth  twist  gear  and  starting 
with  the  circmference  of  the  front  roll  under  the  line,  we  get 
the  twist,  as  follows: 

128X48X45X43 

=  2.966  twist. 

3.534X75X24X30X21 

By  using  the  same  figures,  leaving  out  the  24  tooth  twist 
gear,  we  get  the  twist  constant: 

128X48X45X43 


71.19  twist  constant. 


3.534X75XXX30X21 

Twist  constant  -+-  twist  per  inch  ==  twist  gear. 

71.19  -5-  24  =  2.9*6  twist  per  inch. 
71.19  -T-  2.9i6  =  24  twist  gear. 

In  changing  the  twist  gear  without  the  use  of  the  twist 
constant,  the  following,  rule  holds  good,  remembering  that  the 
twist  and  the  hank  roving  vary  inversely  as  the  size  of  the  twist 
gear;  for  a  larger  twist  gear  gives  less  twist  and  is  used  for  a 
smaller  hank  roving. 

Twist  gear  on  frame  x  twist  on  frame  -4-  twist  desired .  = 
gear  needed. 

Example :  A  frame  has  on  a  30  tooth  twist  gear  and  is  put- 
ting in  2.5  turns  of  twist.  What  size  twist  gear  is  needed  to  give 
3  turns  of  twist? 

30X2.5 

—  =  25  twist  gear  needed. 
3 

In  changing  the  size  of  the  twist  gear  from  the  hank  roving, 


102  COTTON  MILL  MACHINERY   CALCULATIONS. 

the  above  rule  applies  by  substituting  the  square  root  of  the  hank 
roving  in  place  of  the  twist. 

Example:  A  frame  is  running  a  6  H.  R.  with  a  24  tooth 
twist  gear.  What  size  gear  would  be  needed  if  the  roving  was 
changed  to  6.5  H.  R.? 

24  X    V6       24X2.45 

—  = =  23   twist  gear. 

V6:5  2.55 

As  the  basis  of  the  twist  in  the  roving  is  the  square  root  of 
its  hank,  and,  as  the  twist  always  varies  in  accordance  with  this 
basis,  any  change  in  the  size  of  the  twist  gear  must  be  made  on 
the  same  basis,  otherwise  we  are  in  error.  This  is  why,  in  work- 
ing the  above  example,  the  square  root  of  the  hank  roving  was 
used  instead  of  the  hank  roving  itself. 

There  can  be  no  inflexible  rule  given  to  determine  the  correct 
amount  of  twist  required  for  different  rovings.  There  are  several 
conditions  that  will  cause  a  variation  in  the  amount  of  twist  that 
would  be  desirable  to  run :  the  length  of  the  staple,  the  harshness 
or  softness  of  the  fibers  and  the  number  of  previous  drawing 
operations  that  the  cotton  has  been  subjected  to. 

The  usual  rule  for  twist  in  roving  is :  V  H.  R.  x  1.2  =twist 
per  inch. 

This  is 'the  rule  universally  used  for  Uplands  cotton,  and 
meets  the  requirements  in  the  majority  of  cases,  though,  at  times, 
less  twist  can  be  used  to  advantage;  and,  again,  some  cases  will 
require  the  use  of  more  twist.  In  running  longer  stapled  cotton, 
the  amount  of  twist  can  and  has  to  be  decreased,  and  the  amount 
of  this  decrease  grows  more  as  the  length  of  the  staple  increases. 
For  medium  staple,  between  1  inch  and  1}4  inches,  the  following 
rule  will  give  good  results: 

Twist  in  slubber  roving  =  V  H-  R. 

Twist  in  intermediate  roving  =  VH.  R.  X  1.1. 

Twist  on  fine  and  jack  frames  =  VH.  R.  X  1.2. 
For  cottons  of  longer  staple  than  the  above  it  is  possible  to  use 
even  less  twist.  The  sole  object  of  introducing  twist  in  the  roving 
is  simply  to  give  strength  enough  to  hold  it  together  while  being 
put  on  the  bobbin  and  being  pulled  off  in  the  creel  of  the  frame 
following.  Any  more  than  this  amount  is  not  only  unnecessary, 
out  it  causes  a  corresponding  decrease  in  the  production  of  the 
frame,  throws  more  work  on  the  rolls  of  the  following  frame,  and 
may  cause  bad  drawing. 

DIFFERENTIAL  MOTION  OR  COMPOUND. 

The  purpose  of  the  differential  motion  or  compound  is  to  give 
a  suitable  means  for  the  correct  driving  of  the  bobbins.  The  bob- 


PLY  FRAMES. 


103 


bins  must  revolve  as  fast  as  the  spindles  and  enough  in  excess  of 
this  speed  to  wind  on  the  amount  of  roving  delivered  by  the  front 
roll.  As  the  bobbins  increase  in  size,  the  number  of  revolutions 
necessary  to  wind  on  the  roving  decreases,  and  consequently  the 
bobbins  must  decrease  in  speed.  This  decrease  in  bobbin  speed  is 
obtained  by  automatically  changing  the  position  of  the  cone-belt 
on  the  cones  by  means  of  the  tension  gearing,  giving  a  varying 
speed  to  the  bottom  cone.  The  compound  receives  this  variable 
speed  from  the  bottom  cone,  combines  it  with  the  constant  speed 
of  the  main  shaft,  and  delivers  it  as  one  motion  to  the  sleeve  gear. 
The  speed  of  the  bobbins,  due  to  the  motion  of  the  main  shaft,  con- 
sidering the  bottom  cone  as  being  stationary,  is  equal  to  the  speed 
of  the  spindles,  and  consequently  no  winding  would  take  place. 
When  the  bottom  cone  is  in  motion,  the  speed  of  the  bobbins  is 


FIG.  36.    THE  BEVEL  GEAR  DIFFERENTIAL  MOTION  OR  COMPOUND. 

greater  than  the  speed  of  the  spindles,  and  the  roving  is  being 
wound  on  the  bobbins.  This  additional  speed  of  the  bobbins, 
spoken  of  as  the  excess  speed  of  the  bobbins,  is  due  to  the  bottom 
cone  speed  and  is  necessary  to  produce  the  winding.  The  changing 
of  the  position  of  the  cone  belt  changes  the  bottom  cone  speed  and 
the  speed  of  the  compound,  thus  changing  the  speed  of  the  bobbins. 
The  majority  of  American  machine  builders  have  adopted 
one  type  of  compound,  the  old  style  bevel  gear  compound,  a  cut  of 
v/hich  is  shown  in  Fig.  36.  Keyed  on  the  main  shaft,  which  car- 
ries the  twist  gear  and  the  gear  driving  the  spindles,  is  a  bevel  A 
which  drives,  by  means  of  two  idler  gears  C  and  D,  another  bevel 
gear  B,  this  latter  gear  forming  part  of  the  loose  or  "sleeve"  gear, 


104  COTTON  MILL  MACHINERY   CALCULATIONS. 

also  called  the  bobbin  gear.  This  sleeve  consists  of  the  bevel  gear 
B  and  the  spur  gear  of  50  teeth,  which  drives  direct  to  the  bobbins, 
the  two  being  joined  together  by  a  collar  or  sleeve,  the  sleeve  gear 
having  no  connection  whatever  with  the  main  shaft,  being  carried 
on  a  fixed  collar  and  revolving  independently  of  the  main  shaft. 
The  two  idlers,  C  and  D,  serve  simply  to  transmit  motion  from  A 
to  B,  their  axes  being  spokes  of  the  sun-wheel  S,  and  when  S  is 
revolved  around  the  shaft,  C  and  D  will  revolve  about  the  shaft 
with  S.  The  sun-wheel  revolves  independently  of  the  main  shaft 
or  the  fixed  collar,  being  driven  from  the  bottom  cone  at  a  var- 
iable speed. 

It  will  be  seen  that  the  final  speed  of  the  sleeve  gear  B  is  a 
combination  of  the  fixed  speed  of  the  gear  A  and  the  variable 
speed  of  the  gear  S,  the  speed  S  being  the  one  that  gives  the 
excess  speed  to  the  bobbins  and,  also,  the  one  that  is  varied  to  give 
the  decreasing  speed  that  is  demanded  by  the  increasing  size  of 
the  bobbins  while  the  winding  is  taking  place. 

Without  going  into  the  theory  underlying  the  construction  of 
the  compound,  we  can  explain  its  action  by  following  each  motion 
in  detail.  If  we  revolve  A  one  revolution,  the  carriers  C  and  D 
will  transmit  this  direct  to  B  and  B  will  have  one  revolution,  the 
gears  A,  C,  D  and  B  having  the  same  number  of  teeth.  The  di- 
rection of  the  revolution  of  B  will  be  opposite  to  that  of  A.  By 
using  the  signs  -+-  and  —  to  denote  the  direction  of  revolution,  we 
will  get  the  following:  statement  of  the  facts,  it  being  understood 
that  S  is  being  held  stationary. 

Al  +  =  Bl  - 

If  we  consider  A  as  stationary  and  revolve  S  one  revolu- 
tion we  will  get  two  revolutions  to  the  bevel  B.  The  direction  of 
the  revolutions  of  B  will  be  the  same  as  that  of  S.  While  S  re- 
volves, the  idlers  C  and  D  are  being  carried  around  the  shaft  by 
S  and,  as  they  are  in  gear  with  B,  B  will,  of  necessity,  be  carried 
around  the  shaft  in  the  same  direction  as  S  and  will  have  one  revo- 
lution for  one  of  S.  We  can  refer  to  this  revolution  as  due  to  the 
revolving  of  C  and  D  around  the  shaft. 

While  S  is  making  one  revolution  and  carrying  the  gears  C 
and  D  around  the  shaft  with  it,  C  and  D,  being  in  contact  with 
the  fixed  gear  A,  will  have  to  roll  around  the  face  of  A.  Having 
the  same  number  of  teeth,  this  will  cause  C  and  D  to  revolve  on 
their  own  axis  and  will  give  them  one  such  revolution  for  every 
revolution  of  S.  This  will  cause  B  to  have  one  revolution  and  it 
will  be  in  the  same  direction  as  the  gear  S.  We  can  refer  to  this 
revolution  as  due  to  the  revolving  of  C  and  D  on  their  own  cen- 
ters, due  to  their  contact  with  the  gear  A,  while  being  carried 


FLY  FRAMES.  105 

around  the  shaft  by  S.    Then  the  following  statement  will  be  in 
accordance  with  the  above  facts: 

SI  +  =  B2  + 

As  it  is  the  desire  to  revolve  the  sleeve  gear  B  faster  than  the 
fixed  bevel  A  and,  as  the  revolving  of  S  in  the  same  direction  as 
A  would  have  the  effect  of  reducing  the  speed  of  B,  it  will  be  seen 
that  the  sun-wheel  must  revolve  in  the  opposite  direction  to  the 
main  shaft  or  bevel  A.  As  A  revolves  in  (+)  direction  we  must 
revolve  S  in  the  opposite  or  ( — )  direction  and  the  conditions  will 
be  as  follows : 

SI-    =B2- 

Now  take  the  two  equations  for  A  and  S  and  combine  them 
and  we  will  get  the  graphic  statement  of  the  facts: 

Al  +  =  Bl  — 
SI  — =  B2  — 


(A1+)  +  (SI— )  =  B3  — 

With  the  sun-wheel  and  main  shaft  revolving  in  opposite  di- 
rections the  speed  of  B  is  greater  than-  A  and  is  reduced  as  the 
speed  of  S  is  reduced.  If  the  sun-wheel  and  main  shaft  revolve 
in  the  same  direction  the  speed  of  B  would  be  less  than  the  speed 
of  A  and  would  be  increased  as  the  speed  of  the  sun-wheel  is  de- 
creased. This  last  condition  is  found  in  the  old  style  flyer  lead 
frames. 

The  above  can  be  summed  up  in  the  following  words : 

The  speed  of  the  sleeve  gear  is  equal  to  the  speed  of  the  main 
shaft  plus  twice  the,  speed  of  the  sun-wheel. 

The  speed  of  the  sun-wheel  is  greatest  at  the  start  of  a  set 
and  is  decreased  as  the  bobbin  builds,  due  to  the  decrease  in  bottom 
cone  speed  wjiich  occurs  as  the  cone  belt  is  moved  on  the  cones. 

In  Fig.  37  is  shown  a  cut  of  the  Daly,  differential  motion  used 
on  the  Woonsocket  7  by  3  inch  fly  frame.  This  motion  employs 
spur  gears  and  all  parts  revolve  in  the  same  direction,  the  whole 
being  enclosed  so  as  not  to  be  constantly  accumulating  dust  and 

fly. 

On  the  main  shaft  is  an  internal  gear  A  of  80  teeth,  driving 
a  small  gear  of  15  teeth  which  is  compounded  with  a  gear  of  39 
teeth,  both  being  carried  on  a  stud  which  is  fixed  into  the  plate 
gear  D.  This  plate  gear  also  carries  a  bevel  of  57  teeth  which 
drives  direct  to  the  bobbins.  The  39  tooth  gear  is  in  gear  with 
the  24  tooth  gear  C  which  is  on  a  sleeve,  the  other  end  carrying 
a  gear  of  30  teeth,  this  lattt  r  being  driven  from  the  bottom  cone. 


106 


COTTON  MILL   MACHINERY   CALCULATIO 


NS. 


The  gears  24  and  30  are  compounded  together  by  the  sleeve  con- 
necting the  two,  the  whole  being  called  the  sleeve  gear  and  re- 
volves on,  and  in  the  same  direction  with,  the  main  shaft.  The 


FIG.  37.    DALY  DIFFERENTIAL. 

bobbin  or  plate  gear  D  revolves  on  the  collar  of  the  sleeve  gear  and 
in  the  same  direction  as  the  main  shaft. 

As  in  the  former  case,  there  are  two  motions  which  are  com- 
bined into  one ; 

First:     The  fixed  constant  speed  of  the  main  shaft  gear  A. 

Second:  The  variable  speed  of  the  sleeve  gear  C,  which 
comes  from  the  bottom  cone  and  gives  to  and  regulates  the  ex- 
cess speed  of  the  bobbins. 

If  we  consider  the  effect  of  these  two  motions  separately  on 
the  gear  D,  we  will  be  able  to  understand  the  operation  of  the  com- 


FLY  FRAMES.  107 

pound.  While  A  is  moving  and  C  is  held  still,  A  carries  the  com- 
pound gear  15  and  39  around  with  it,  because  it  cannot  revolve  on 
its  own  axis,  due  to  the  fact  that  the  24  and  39  tooth  gears  are  in 
contact  and  the  24  tooth  gear  is  stationary.  While  the  compound 
gear  of  15  and  39  teeth  is  being  carried  around  the  shaft  by  the 
movement  of  the  gear  A,  the  39  tooth  gear  is  meshing  with  the  24 
tooth  gear,  which  will  cause  the  15  and  39  tooth  gear  to  revolve 
on  its  own  axis.  This  action  will  cause  a  lagging  behind  of  the 
gear  D  or  a  slipping  ahead  of  the  gear  A.  Now,  if  A  is  given  one 
complete  revolution,  it  will  be  seen  that  the  gear  D  will  not  revolve 
a  full  revolution,  due  to  the  compound  gear  15  and  39  revolving  on 
its  own  axis  caused  by  the  39  tooth  gear  rolling  around  the  face 
of  the  stationary  gear  of  24  teeth  and,  to  revolve  A  far  enough  to 
cause  a  complete  revolution  to  D,  the  39  tooth  gear  will  revolve  en- 
tirely around  the  24  tooth  gear  and  make  24/39  of  a  revolution  on 
its  own  axis,  hence  the  15  tooth  gear  compounded  with  the  39  tooth 
gear  will  make  the  same  fraction  of  a  revolution.  This  will  cause 
the  gear  A  to  advance  ahead  of  the  gear  D  by  the  following  frac- 
tion : 

24       15 

—  X  —  =  .115. 

39       80 

Then,  when  A  makes  1.115  revolutions,  D  will  make  1  revolu- 
tion and  while  A  is  making  1  revolution  D  will  make  .896  of  a  revo- 
lution. Now,  if  we  express  the  speed  of  D,  due  to  the  speed  of  A, 
in  terms  of  A,  we  get  the  following: 

D  =  A  X  .896. 

Now  take  the  second  condition  and  suppose  A  is  still  and  re- 
volve C.  When  C  is  revolved  the  gear  of  24  teeth  gives  motion  to 
the  39  and  the  15  tooth  compound  gear  and  causes  it  to  revolve  on 
its  own  axis.  This  will  cause  the  15  tooth  gear  to  be  moved 
around  the  internal  gear  A  of  80  teeth  and  give  the  gear  D  a  part 
of  a  revolution  for  every  revolution  of  C,  expressed  by  the  value 
of  the  train  of  gearing: 

24X15 

=  .115. 

39X80 

Then  the  speed  of  D,  due  to  the  speed  of  C  and  expressed  in 
terms  of  C,  will  be  as  follows : 

D  =  CX  .115. 

Now  combining  the  two  speeds  of  D,  due  to  the  speeds  of  A 
and  C,  in  terms  of  both  A  and  C,  we  have : 

The  speed  of  D  =  (A  X  .896)  +  (C  X  .115). 


108  COTTON  MILL  MACHINERY   CALCULATIONS. 

The  value  of  the  train  of  gearing  between  the  main  shaft  and 
the  spindles  and  between  the  gear  D  and  the  bobbins,  is  such  as  to 
give  the  same  speed  to  the  spindles  and  bobbins  when  C  is  station- 
ary, then  it  will  be  seen  that  when  C  revolves,  the  bobbins  have 
a  speed  faster  than  the  spindles  and  are  winding  on  the  roving  and 
that,  when  the  speed  of  C  is  reduced  the  speed  of  the  bobbins  is 
reduced. 

WINDING. 

The  winding  of  the  roving  on  the  bobbin  is  accomplished  by 
the  excess  speed  of  the  bobbin  which  is  gotten  from  the  bottom 
cone  by  means  of  the  compound.  The  speed  of  the  bottom  cone  is 
regulated  by  the  position  of  the  cone  belt  which  is  automatically 
changed  by  the  tension  gearing  at  the  end  of  each  layer  wound. 
Consider  the  bobbin  to  be  1  inch  in  diameter  when  empty  and  4 
inches  when  full,  then  the  bobbin  will  increase  in  uniform  amounts 
from  1  inch  to  4  inches,  a  total  increase  in  diameter  of  3  inches 
which,  supposing  the  cones  to  be  30  inches  long,  is  an  increase  in 
diameter  of  1/10  inch  for  every  inch  of  belt  traverse,  or  1/2  inch 
increase  for  a  belt  traverse  of  5  inches,  or  1/6  the  total  length  of 
the  cones. 

The  above,  although  true,  is  misleading,  as  the  statement  is 
often  made,  based  on  the  above  facts,  that  the  speed  of  the  bottom 
cone,  and  hence  of  the  bobbins,  decreases  in  regular  amounts  for 
each  layer  wound  from  start  to  finish  of  a  set.  It  is  true  that  the 
increase  in  bobbin  diameter  is  in  regular  amounts  for  each  layer 
wound,  or  each  movement  of  the  cone  belt,  but  the  proportional  in- 
crease in  bobbin  diameter  is  not  regular,  being  larger  at  the  begin- 
ning than  at  the  end  of  a  set,  hence,  the  variation  in  speed  of  bot- 
tom cone  and  bobbin  is  not  re^ilar,  but  decreases  as  the  bobbin 
builds  by  a  lesser  amount  for  each  layer  wound.  This  will  be  seen 
when  we  consider  that,  at  the  start  of  a  set,  we  are  winding  the 
roving  on  a  bobbin  that  is  only  1  inch  in  diameter,  while,  at  the 
end  of  a  set  the  diameter  of  the  bobbin  is  4  inches,  hence,  the  rela- 
tive increase  in  bobbin  diameter,  by  the  addition  of  one  layer  of 
roving,  must  be  greater  when  the  bobbin  is  small  than  when  it  is 
large. 

When  the  bobbin  has  become  2  inches  in  diameter,  it  has 
wound  on  a  thickness  of  roving  of  1  inch,  which  is  one-third  the 
total  increase  in  the  bobbin  diameter,  so  the  belt  must  have  travel- 
ed one-third  the  length  of  the  cones.  Now,  the  bobbin  at  this  point 
is  one-half  its  full  diameter,  so  its  excess  speed  and,  also,  the 
speed  of  the  bottom  cone,  must  have  decreased  by  one-half,  as  it 
rfow  takes  only  one-half  the  number  of  revolutions  of  the  bobbin 
to  wind  on  the  delivery  of  the  front  roll.  The  diameter  of  the  bot- 


FLY  FRAMES. 


109 


torn  cone  at  this  point  will  be  the  same  as  that  of  the  top  cone. 

The  following  facts  are  true  and  demonstrable: 

First:  Straight  faced  cones  will  not  give  the  proper  results 
when  applied  to  fly  frames. 

Second :  The  speed  of  the  bottom  cone  and  bobbin  .toes  not  de- 
crease in  regular  amounts  for  every  layer  wound  on  the  bobbin, 
but  must  decrease  in  inverse  ratio  to  the  proportional  increase  of 
bobbin  diameter. 

Third :  At  all  opposite  points  of  a  correct  pair  «.»f  cones  the 
sum  of  the  top  and  bottom  cone  diameters  will  be  equal,  the  cones 
will  give  a  variable  decrease  in  the  speed  of  the  bobbin,  this  de- 


FIG.  38.  SPINDLE  AND  BOBBIN  GEARING.    LOWELL  7  BY 
FLY  FRAME. 


INCH 


crease  being  larger  at  the  start  of  a  set  than  at  the  end  and  the 
outline  of  the  cones  will  be  concave  and  convex  curves,  equal  diam- 
eters coming  at  one-third  the  length  of  the  cones,  measured  from 
the  large  end  of  the  top  cone.  The  top  cone  is  concave  and  the 
bottom  cone  convex,  the  greatest  curve  in  their  outlines  coming  at 
the  large  end  of  the  top  and  the  small  end  of  the  bottom  cone. 

As  the  total  speed  of  the  bobbin  is  governed  by  the  delivery 
of  the  front  roll,  the  size  of  the  bobbin  and  the  speed  of  the  spindle, 
the  required  speeds  of  bobbin  and  bottom  cone  can  be  figured  and 
the  correct  diameters  determined  at  any  point  in  the  build  of  a 
bobbin. 


110  COTTON   MILL  MACHINERY   CALCULATIONS. 

Fig.  38  is  a  diagram  of  the  spindle  and  bobbin  Bearing  of  a 
fine  fly  frame  built  by  the  Lowell  Machine  Shop.  This  frame  is  5*4 
inches  space  and  7  inches  traverse  and  builds  a  bobbin  7  by  3 1/2 
inches,  the  diameter  of  the  empty  bobbin  being  1%  inches.  Main 
shaft  speed  at  400  R.  P.  M.  and  using  a  30  tooth  twist  gear,  gives 
a  top  cone  speed  of  200  R.  P.  M.  The  front  roll  speed  is : 

400X30X97 

—  =  118.29  R.  P.  M. 
60X164 

The  front  roll  is  IVs  inches  in  diameter,  ana  will  deliver 
418.04  inches  of  roving  per  minute.  The  spindle  speed  is : 

400X60X46 


=  1254.54   R.   P.   M. 


40X22 

As  we  start  with  an  empty  bobbin  diameter  of  >.  inch,  it  will 
wind  on  3.1416  inches  of  roving  for  every  revolution  that  it  makes, 
hence,  the  speed  of  the  empty  bobbin  to  wind  on  the  delivery  of 
the  front  roll  is  as  follows : 

418.04  H-  3.1416  =  133.065  R.  P.  M. 

This  allows  for  no  increase  in  bobbin  speed  to  provide  for 
the  proper  tension  on  the  roving  and  should  be  increased  about 
1.67  per  cent,  which  gives  135.27  R.  P.  M.  of  bobbin  to  wind  on 
the  delivery  of  the  front  roll.  This  is  the  excess  speed  of  the  bob- 
bin and  must  be  added  to  the  speed  of  the  spindle  to  give  the  total 
speed  of  the  bobbin,  as  follows: 

1,254  +  135.27  =  1389.81  R.  P.   M.   of  bobbin. 

Take  this  figured  speed  of  the  bobbin  as  a  starting  point,  the 
following  figures  will  give  the  speed  of  the  sleeve  gear : 

1389.81X22X42 


=  443.12  R.  P.  M. 


46X63 

The  speed  of  the  sun-wheel  equals  one-half  the  difference  be- 
tween the  speeds  of  the  main  shaft  and  sleeve  gear,  so : 

(443.12  —  400) 

—  =  21.56  R.  P.   M.  of  sun-wheel. 
2 

speed  of  the  bottom  cone  at  the  start  is  found  from  the 
speed,  as  follows: 

21.56X150X68 

—  =  399.8  R.  P. 'M.  or  practically  400  R.  P.  M. 
25X22 

By  taking  the  bobbin  at  any  diameter  during  its  build  and  fol- 


FLY  FRAMES.  Ill 

lowing  the  above  method  of  figuring,  we  can  determine  the  bobbin 
and  bottom  cone  speeds. 

Although  the  frame  builds  a  bobbin  only  31/2  inches  in  diam- 
eter when  full,  starting  with  an  empty  bobbin  diameter  of  1% 
inches,  it  is  necessary  to  make  the  calculations  for  a  bobbin  smaller 
at  the  start  and  larger  at  the  finish  than  is  actually  used,  as  it  is 
impossible  to  run  the  cone  belt  on  the  extreme  end  diameters,  as 
would  be  required  if  we  made  the  calculation  with  the  same  sizes 
to  empty  and  full  bobbin  that  is  actually  run  on  the  frame  and, 
also,  to  have  ample  room  at  the  ends  of  the  cones.  This  enables 
the  starting  and  finishing  points  of  the  cone  belt  to  be  changed  to 
suit  varying  conditions. 

The  following  table  gives  the  required  speeds  of  the  bobbin 
and  bottom  cone  and  the  diameter  of  the  bobbin  at  the  start  of  a 
set  and  after  each  belt  movement  of  5  inches : 

Speed  of  bottom  cone.          Speed  of  Bobbin.         Diam.  of  Bobbin. 

Start,  400  1389.81  1  inch. 

1st  point,  266.66  1344.77  li/2  inches. 

2nd  point,  200  1322.14  2  inches. 

3rd  point,  160  1308.68  2i/2  inches. 

4th  point,  133.33  1299.56  3  inches. 

5th  point,  114.33  1293.22  3V2  inches. 

6th  point,  100  1288.34  4  inches. 

These  figures  were  obtained  from  calculations  based  on  the 
actual  delivery  of  the  front  roll,  spindle  speed  and  the  diameter  of 
the  bobbin,  allowing  for  tension  during  the  winding  of  the  roving. 
This  last  is  a  variable  quantity  and  there  are  other  factors  to  be 
taken  into  consideration,  still  the  above  speeds  are  accurate 
enough  for  all  practical  purposes  and  are  very  close  to  those  that 
would  be  found,  under  the  same  conditions,  in  the  running  of  the 
frame. 

If  we  now  figure  a  pair  of  cones,  based  on  the  speeds  in  the 
above  table,  we  will  get  the  results  shown  in  Fig.  39.  This  shows 
a  pair  of  cones,  with  the  cone  diameters,  bottom  cone  and  bobbin 
speeds  for  every  belt  movement  of  5  inches. 

The  speed  of  the  bottom  cone  varies  in  inverse  ratio  to 'the 
proportional  increase  in  bobbin  diameter,  then,  the  following  rule 
for  figuring  bottom  cone  speed  is  correct. 

The  speed  of  the  bottom  cone  at  start  x  diameter  of  empty 
bobbin  -+-  the  diameter  of  the  bobbin  at  any  point  =  the  speed  of 
the  bottom  cone  at  that  point. 

From  this  we  find  that  the  bottom  cone  at  the  first  point,  or 


112 


COTTON   MILL   MACHINERY   CALCULATIONS. 


at  the  end  of  a  traverse  of  5  inches,  will  have  a  speed  of  266.66 
R.  P.  M.  as  follows: 

400X1 

=  266.66 

1.5 

The  same  method  of  calculation  was  used  to  get  the  bottom 
cone  speeds  at  the  remaining  points  and,  in  every  case,  it  will  be, 


BOTTOM  COME 


/V  D/AM&TS/ 


FIG.  39. 


A  PAIR  OF  CONES  FIGURED  ON  THE  BASIS  OF  THE  TABLE 
OF  SPEEDS  GIVEN. 


noted  that  these  speeds  will  coincide  with  those  shown  in  the  table. 

With  the  speeds  of  bottom  and  top  cones  known,  the  diameters 
of  the  two  cones  were  found  by  the  following  rules : 

Sum  of  cone  diameters  x  bottom  cone  speed  at  any  point  -f 
sum  of  cone  speeds  at  that  point  =  the  top  cone  •  diameter. 

The  sum  of  the  cone  diameters  —  top  cone  diameter  =  the 
bottom  cone  diameter. 

Then,  taking  the  figures  for  the  first  point,  the  sum  of  the  cone 
diameters  being  8.625,  we  will  get  the  following  as  the  cone  diam- 
eters at  this  point: 

8.625X266.66 

—  =  4.928 
200  +  266.66 
8.625  —  4.928  =  3.697 

Then  the  top  cone  diameter  will  be  4.928  inches  and  the  bot- 
tom cone  diameter  will  be  3.697  inches.  The  diameter  of  the  two 
cones  at  the  other  points  were  figured  by  the  same  method. 


PLY  FRAMES.  113 

It  will  be  noticed  that  at  the  second  point,  or  when  the  belt 
has  moved  10  inches  or  1-3  of  the  length  of  the  cones,  the  bobbin 
has  increased  1  inch  in  diameter  of  1-3  its  total  increase  and  is 
l/2  its  full  diameter,  the  speed  of  the  bottom  cone  is  J/2  its  speed  at 
the  start,  and-  the  diameters  of  the  two  cones  are  equal.  This  fact 
proves  that  straight  faced  cones  cannot  be  used  as  their  equal 
diameters  come  at  the  middle  of  the  cones.  It  will  be  also  noticed 
that  the  diminution  in  the  speed  of  the  bobbin  is  greatest  during 
the  first  movement  of  the  belt,  this  decrease  growing  smaller  as 
the  end  of  the  set  is  reached  by  a  varying  amount.  This  is  the 
actual  condition,  for  the  proportional  increase  in  bobbin  diameter 
is  greatest  at  the  start  of  a  set,  when  the  bobbin  is  small,  although 
the  actual  increase  in  bobbin  diameter  is  practically  the  same  for 
each  layer  wound. 

It  will  be  noticed  that,  the  results  obtained  from  this  pair  of 
developed  cones  are  similar  to  those  as  figured  from  the  front  roll 
delivery,  hence,  the  cone  outlines  must  be  correct-  For  compari- 
son, select  the  figures  for  the  second  point  and  start  with  the  main 
shaft  speed  and  figure  the  total  speed  of  the  bobbin  and  compare 
with  the  required  speed  as  given  in  the  table  or  with  the  speed  as 
shown  in  Fig.  39.  The  speed  of  sun-wheel  is : 

400X30X4.31X22X68X25 

—  =  10.78   R.   P.   M. 
60X4.31X68X68X150 

The  speed  of  the  sleeve  gear  is  400  +  (2  X.  10.78)  =421.56 
R.  P.  M.  Then  the  speed  of  the  bobbin  is  obtained  as  follows : 

421.56X63X46 

—  ==1322.16  R.   P.   M. 
42X22 

This  speed  is  practically  the  same  as  obtained  by  our  former 
figures,  and  using  the  above  method,  and  figuring  the  bobbin  speed 
at  any  point,  will  give  results  that  will  be  practically  the  same  as 
those  found  before.  This  shows  that  the  cone  diameters  given  in 
Fig.  39  must  be  correct  and  their  method  of  development  meets 
the  requirements  in  the  case. 

TENSION  GEARING. 

We  have  already  found  that  the  shape  of  the  cones  was  such 
that,  for  each  layer  wound  on  the  bobbin,  the  cone  belt  is  moved 
an  equal  distance  along  the  face  of  the  cone,  giving  the  correct  de- 
crease in  bobbin  speed  and  a  uniform  tension  from  start  to  finish 
of  a  set-  The  amount  of  this  traverse  would  naturally  be  the  length 
of  the  cone  used,  from  start  to  finish  of  the  set,  divided  by  the 
number  of  layers  put  on  the  full  bobbin.  No  rule  can  be  given  to 


114  COTTON  MILL  MACHINERY   CALCULATIONS. 

determine  the  proper  tension  gear  for  different  sizes  of  roving 
that  will  work  under  all  conditions,  as  the  tension  depends  largely 
upon  the  amount  of  twist  in  the  roving  and  the  lay  of  the  roving 
on  the  bobbin.  A  change  of  atmospheric  conditions  will  affect 
the  tension,  for  roving  that  will  run  all  right  on  a  damp  day  may 
be  too  tight  on  a  clear,  dry  day,  necessitating  a  change  of  one  or 
two  teeth  in  the  size  of  the  tension  gear- 

The  amount  of  twist  in  the  roving  also  influences  the  tension 
to  a  certain  extent,  for,  if  the  roving  is  hard  twisted,  its  diameter 
is  smaller  and  consequently,  the  bobbin  increases  slower  in  diam- 
eter, necessitating  a  slower  decrease  in  speed. 

The  size  of  the  rail  or  lay  gear,  governing  the  speed  at  which 
the  rail  is  traversed,  thus  determining  the  closeness  of  the  coils  in 
each  layer,  also  has  a  tendency  to  affect  the  tension.  If  the  lay 
gear  is  too  large,  the  rail  speed  will  be  too  fast  and  the  coils  would 
be  more  open,  allowing  the  next  layer  of  roving  to  draw  down  be- 
tween the  coils,  therefore,  the  diameter  of  the  bobbin  would  not 
increase  as  rapidly  with  each  layer  wound.  This  would  require  a 
slower  decrease  in  bobbin  speed  and  call  for  the  use  of  a  smaller 
tension  gear  than  we  would  naturally  expect. 

From  the  above  facts,  the  conditions  governing  the  tension 
on  the  roving  are  seen  to  be  of  such  a  variable  nature  that  the  final 
judge  of  the  correctness  of  the  tension  on  the  roving  must  be  its 
appearance  as  the  frame"  runs,  and  the  tension  gear  must  be  chang- 
ed to  suit  the  conditions  regardless  of  how  far  from  its  calculated 
size  we  may  have  to  vary. 

Fig.  40  shows  the  plan  of  gearing  on  a  12  x  6  inch  Saco-Pettee 
slubber.  The  upright,  or  tumbling  shaft,  carries  a  double  thread- 
ed worm,  driving  into  a  32  tooth  worm  gear.  On  the  stud  with 
this  worm  gear  is  a  60  tooth  gear  driving  into  a  50  tooth  gear.  On 
the  stud  with  this  gear  is  the  tension  gear,  gearing  direct  into  the 
cone  rack.  After  the  winding  of  each  layer  on  the  bobbin  the 
tumbling  shaft  is  revolved  V£  a  revolution  by  the  gear  on  the  end 
of  the  top  cone  shaft.  This  causes  the  worm  gear  to  move  one 
tooth,  thus  moving  the  belt  a  certain  distance  on  the  cones,  this 
distance  depending  upon  the  size  of  the  tension  gear. 

If  we  assume  the  main  shaft  speed  as  250  R.  P.  M.,  with  a 
56  tooth  twist  gear  on  and  the  frame  to  be  running  .64  H.  R.,  then 
the  top  cone  speed  will  be :  • 

250X56 

—  -=304.35   R.   P.   M. 
46 

The  belt  starts  on  the  top  cone  2.75  inches  from  the  end.  The 
diameter  of  the  top  cone  at  this  point  is  6.75  inches  and  the  corre- 
sponding diameter  of  the  bottom  cone  is  3.75  inches,  giving  a  ratio 


FLY  FRAMES.  115 

between  the  two  of  1.8.  Then  the  bottom  cone  speed  at  the  start  is : 

304.35  X  1.8  =  547.83  R.  P.  M. 

When  the  bobbin  is  full  its  diameter  is  6  inches  and  the  belt 
has  moved  its  full  traverse  on  the  cones.  The  diameter  of  the 
empty  bobbin  is  1%  or  1.875  inches,  hence,  the  bottom  cone  speed 
at  this  point  will  be : 

547.83X1.875 

—  =  171.19  R.  P.  M. 
6 

Knowing  the  top  and  bottom  cone  speed,  we  can  find  the  top 
cone  diameter  by  the  following: 

10.5X171.19 

—  =  3.77  inches  for  the  top  cone  diameter  when  the  bobbin 
304.35  +  171.19  [is  6  inches  in  diameter  or  full. 

As  the  point  on  the  top  cone  where  the  diameter  is  3.77  inches 
is  28.5  inches  from  the  point  where  the  belt  starts,  then  the  belt 
and  belt  rack  must  move  28.5  inches  while  building  a  full  bobbin. 
There  are  32  teeth  in  10  inches  of  rack  or  3.2  teeth  in  every  inch. 
Therefore,  the  rack  must  move :  28.5  x  3.2  =  91.2  teeth  in  order 
to  move  the  belt  28.5  inches. 

There  are  eight  coils  per  inch  on  the  bobbin  ( V.64  x  10  =  8) 
and,  as  the  layers  per  inch  are  four  times  the  coils  per  inch,  there 
will  be  32  layers  per  inch  on  the  bobbin.  The  diameter  of  the 
empty  bobbin  is  1%  inches,  and  the  diameter  of  the  full  bobbin  6 
inches,  therefore,  there  is  4Vp,  inches  of  roving  put  on  the  bobbin, 
or  2  1/16  inches  on  each  side,  to  build  it  out  to  6  inches  in  diam- 
eter. Then :  2  1/16  x  32  =  66  layers  of  roving  wound  on  the  bob- 
bin, which  calls  for  66  reversions  of  the  rail  and  66  movements  of 
the  cone  belt  rack. 

The  tumbling  shaft  makes  */£  a  revolution  for  every  rever- 
sion of  the  rail,  or  for  every  movement  of  the  belt  rack,  then  33 
revolutions  of  tumbling  shaft  will  be  required  for  the  66  rever- 
sions of  the  rail.  Therefore,  to  wind  on  the  66  layers  of  roving, 
or  to  move  the  belt  rack  the  28.5  inches  necessary,  it  will  require 
2.47  revolutions  of  the  stud  carrying  the  tension  gear,  as  follows : 

33X2X60 

•  =  2.47. 

32X50 

As  there  is  a  total  of  91.2  teeth  used  in  the  rack  in  traversing 
the  belt  the  necessary  28.5  inches,  there  will  be  required  37 
teeth  in  the  tension  gear,  as  follows:  91.2-^-2.47  =  36.9  or  37 
teeth.  Then  :  V  .64  x  37  =  29.6  tension  constant. 

Rule  xor  using  tension  constant: 

Constant  -f-  VHR  —  tension  gear. 


116 


COTTON   MILL   MACHINERY   CALCULATIONS. 

•/•-Vcb'  &  OSS 


TL               f«      .  nr 

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0 

i 

4H 

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5 

0 

1 

k 

W                                                    k 

sl                    I 

VJ 
0 

J 

II  ' 

N  ni 


1*1 

10 

£ 


FIG.  40.    SACO-PETTEE  12  x  6  SLUBBER. 


FLY  FRAMES.  117 

LAY  GEARING. 

Referring  again  to  Fig.  40,  the  bottom  cone  drives  the  take- 
up  shaft,  which,  through  a  train  of  bevel  and  spur  gears,  drives 
the  lay  shaft  carrying  the  lay  gear.  This  gear  is  also  called  the 
traverse  or  rail  gear.  The  lay  gear,  by  a  train  of  spur  gears, 
drives  the  lifting  shaft.  On  the  lifting  shaft  is  a  12  tooth  pinion 
in  gear  with  the  lifting  arm  or  segment  that  raises  and  lowers 
the  rail. 

As  we  found  before,  the  bottom  cone  has  a  speed  at  the  start 
of  547.83  R.  P.  M.,  then  the  speed  of  the  take-up  shaft  will  be : 

547.83X16 

—  -=182.61  R.  P  .M. 
48 

By  following  the  train  of  gears  between  the  take-up  shaft 
and  the  lay  shaft,  we  get  the  speed  of  the  lay  shaft  to  be : 

182.61X18X20X30 

—  =-23.48  R.  P.  M. 
40X70X30 

The  above  is  the  calculated  speed  of  the  lay  shaft  that  would 
be  present  under  the  above  conditions.  The  correct  lay  of  the  rov- 
ing on  the  bobbin  is  based  on  the  square  root  of  the  roving  and, 
under  ordinary  conditions,  will  not  be  far  from  the  results  obtain- 
ed from  the  following  rule : 

Coils  per  inch  =  square  root  of  the  H.  R.  X  10. 

As  we  have 'assumed,  in  the  calculation  for  the  tension  .e-ear, 
that  the  frame  is  running  on  .64  H.  R.,  the  coils  per  inch  will  be : 
V.64  X  10  =  8,  that  is,  8  strands  of  .64  H.  R.  will  lie  in  one  inch 
of  bobbin  length. 

The  bobbin,  when  emnty,  is  1.875  inches  in  diameter,  or  5.89 
inches  in  circumference,  then  every  coil  on  the  bobbin  will  have 
5.89  inches  of  roving  in  it  and,  as  there  are  8  coils  per  inch,  the 
bobbin  will  wind  up :  5.89  x  8  =  47.12  inches  of  roving  for  every 
inch  of  rail  traverse. 

The  speed  of  the  front  roll  is  found  as  follows : 

250X56X71 

—  =  166.25  R.   P.   M. 
46X130 

The  front  roll  is  1  3/16  inches  in  diameter  or  3.73  inches  in 
circumference,  then:  166.25X3.73  =  620.113  inches  of  roving 
will  be  delivered  by  the  front  roll  per  minute.  By  dividing  the  de- 
livery of  the  front  roll  per  minute  by  the  amount  of  roving  wound 
on  the  bobbin  per  inch  of  traverse,  we  will  get  the  speed  at  which 
the  rail  will  have  to  move:  620.113  -f-  47.12  =  13.18  inches  per 
minute. 


118  COTTON  MILL  MACHINERY  CALCULATIONS. 

The  lifting  gear  has  12  teeth  and  moves  the  lifting  arm  13.26 
inches  during  a  12  inch  traverse  of  rail.  The  teeth  on  the  lifting 
arm  are  placed  10  in  6.5  inches  or  each  tooth  occupies  a  space  of 
.65  inch,  then :  .65  x  12  =  7.8  inches  which  the  lifting  arm  moves 
for  every  revolution  of  the  lifting  gear.  As  the  lifting  arm  has  to 
move  a  total  of  13.26  inches  for  a  full  traverse  of  the  rail,  so: 
12.26  ~-  7.8  =  1.7  revolutions  of  lifting  gear  to  a  full  12  inch  tra- 
verse of  the  bobbin  rail. 

Now,  if  the  bobbin  rail  travels  at  the  rate  of  13.18  inches  per 
minute  and  it  takes  1.7  revolutions  of  the  lifting  gear  to  traverse 
the  rail  12  inches,  then  the  speed  of  the  lifting  gear  or  shaft  will  be 
1.86  R.  P.  M.,  as  follows: 

13.18 

—  X  1.7  =  1.86  R.  P.  M. 
12 

By  following  the  train  of  gearing,  we  get  the  speed  of  the 
1 10  tooth  crown  gear  to  be : 

1.86X71X47 

—  =  4.949  R.  P.  M. 
33X38 

and  the  total  number  of  teeth  used  on  the  crown  gear  will  be: 
4.949  x  no  =  544.39  teeth  per  minute. 

As  the  lay  gear  drives  this  crown  gear  and  we  have  found  the 
speed  of  the  lay  shaft  to  be  23.48  R.  P.  M.,  we  get  the  number  of 
teeth  in  the  lay  gear  as  follows: 

544.39  H-  23.48  =  23  tooth  lay  gear. 
Then:      V.64  X  23  =  18.4  lay  constant. 

Rule  for  using  the  lay  constant: 

Constant  -j-  VHR  =  lay  gear. 

The  following  rule  is  useful  in  changing  the  hank  roving  on 
the  frames  and  applies  to  both  the  lay  and  tension  gears : 

V#.  R.  on  frame  x  gear  on  frame  ~-  ^/H.R.  desired  =  gear 
needed. 

It  is  understood  that,  in  using  the  rule,  there  is  no  change 
to  be  made  in  the  size  of  the  roving  on  the  back  of  the  frame. 

TAKE-UP  GEARING. 

Referring  to  Fig.  40,  the  bottom  cone  drives  the  take-up 
shaft  by  a  16  into  a  48  tooth  gear  at  a  speed,  as  we  have  before 
found,  of  182.61  R.  P.  M.  The  take-up  shaft  carries  the  take-up 
gear  which  drives  the  sun-wheel  and  provides  for  the  excess 


FLY   FRAMES.  119 

speed  of  the  bobbin  necessary  to  wind  on  the  delivery  of  the  front 
roll.  As  the  excess  speed  of  the  bobbin  is  the  only  speed  we  need 
to  consider,  it  being  the  only  one  affected  by  the  take-up  gear, 
the  total  speed  of  the  bobbin  need  not  be  figured. 

We  have  found  that  the  front  roll  delivers  62'0.113  inches 
of  roving  per  minute  and  the  circumference  of  the  1%  inch  bob- 
bin to  be  5.89  inches,  hence,  the  bobbin  will  have  to  make  105.3 
R.  P.  M.  to  wind  on  the  roving  delivered  by  the  front  roll.  This 
is  the  excess  or  winding  speed  of  the  bobbin,  derived  from  the 
bottom  cone  and  being  entirely  independent  of  the  bobbin  speed 
obtained  from  the  main  shaft. 

Starting  with  this  speed  and  following  the  train  of  gears 
back  to  the  sleeve  gear,  we  get  the  following : 

105.3X27X46 

=  47.6  R.  P.  M. 

55X50 

-This  47.6  R.  P.  M.  represents  the  speed  of  the  sleeve  gear 
obtained  from  the  sun-wheel.  This  is  not  considering  the  speed  of 
the  sleeve  gear  derived  from  the  speed  of  the  main  shaft.  Then 
the  speed  of  the  sun-wheel  is  47.6  -=-  2  =  23.8  R.  P.  M.  There 
are  140  teeth  in  the  sun  wheel,  so  the  speed  of  tLe  sun-wheel, 
multiplied  by  its  number  of  teeth  and  divided  by  the  speed  of  the 
take-up  shaft,  will  give  the  size  of  the  take-up  gear  to  use. 

23.8X140 

=  18.2  or  18  teeth  in  the  take-up  gear. 

182.61 

After  the  proper  take-up  gear  has  been  put  on  and  the  cor- 
rect starting  position  of  the  cone-belt  determined  to  give  'the 
proper  tension  on  the  roving  during  the  winding  of  the  first  layer 
on  the  bobbin,  there  is  no  need  to  change  the  size  of  the  gear. 

By  a  similar  method  of  calculation,  the  cone  gear  can  be 
found  on  those  frames  that  use  this  gear  as  a  change  point  instead 
of  a  take-up  gear.  There  is  one  disadvantage  in  changing  the  gear 
on  the  bottom  cone,  to  change  the  speed  of  the  bobbin  at  the  start, 
which  is  not  present  when  the  take-up  gear  is  changed  and,  that 
is,  when  it  ever  becomes  necessary  to  change  the  <*one  gear,  we 
change  the  value  of  the  train  of  gearing  that  drives  the  rail  and 
the  lay  of  the  roving  on  the  bobbin  is  altered  to  a  certain  ex- 
tent. When  the  take-up  gear  is  altered,  the  only  change  made 
is  in  the  speed  of  the  bobbin  and,  as  this  is  present  throughout 
the  complete  building  of  the  bobbin  and  all  the  other  motions 
are  left  as  before,  the  tension  gearing  or  traversing  of  the  cone 
belt  is  in  no  wise  affected.  No  change  gear  should  ever  be  placed 
in  such  a  position  that  a  change  in  its  size  will  affect  the  value 


120  COTTON   MILL  MACHINERY   CALCULATIONS. 

of  any  other  train  of  gearing  that  is  controlled  by  another  change 
gear. 

TAPER  GEARING. 

The  builder  is  carried  in  a  suitable  frame  mounted  on  the 
bobbin  rail  and  moves  with  the  rail.  The  two  sliding  builder  jaws 
are  mounted  on  a  right  and  left  handed  screw,  so  that,  turning 
the  screw  will  cause  the  builder  jaws  to  move  closer  together  or 
farther  apart,  thus  decreasing  or  increasing  the  length  of  the 
traverse.  On  the  end  of  this  screw  is  connected  a  square  rod, 
which  slides  through  a  square  hole  in  the  center  of  the  taper  gear, 
this  latter,  gearing  direct  into  the  belt  rack.  Now,  as  the  belt 
•ack  is  moved  at  the  end  of  each  layer  wound,  the  taper  gear  is 
Turned,  thus  turning  the  screw  and  closing  the  builder  jaws  to- 
gether, thus  causing  the  next  layer  wound  to  be  shorter  than  the 
previous  one.  This  is  repeated  after  each  layer  and  causes  a 
gradual  reduction  in  the,  length  of  the  layers  put  on,  giving  the 
taper  on  the  ends  of  the  bobbin. 

The  traverse  is  shortened  y»  coil  at  each  reversion  of  the 
rail  and,  as  there  are  66  reversions  to  the  rail  to  wind  the  full 
bobbin,  the  traverse  will  be  shortened  a  total  of  33  coils.  The 
roving  lays  8  coils  per  inch,  hence,  the  total  shortening  of  the 
traverse  is  4Vp,  inches.  One  revolution  of  the  taper  gear  closes 
the  builder  jaws  %  inch,  then :  4.125  -f-  .75  =  5.5  revolutions 
needed  to  the  taper  ?ear.  The  total  traverse  of  the  cone  belt 
rack,  in  building  a  full  bobbin,  is  28.5  inches  or  91.2  teeth,  conse- 
quently, the  size  of  the  taper  gear  will  be:  91.2  -4-  5.5  =  16.6  or 
17  teeth. 

PRODUCTION. 

The  production  of  a  fly  frame  depends  upon  the  spindle 
speed,  or  amount  of  twist  put  into  the  roving,  the  number  of  sets 
or  doffs  per  day,  the  number  of  ends  broken,  the  number  of  spin- 
dles to  a  frame  and  the  general  efficiency  of  the  operative.  As  all 
of  the  above  conditions  are  variable,  it  is  almost  impossible  to 
give  a  definite  statement  in  regard  to  the  amount  of  time  lost 
during  the  operation  of  a  frame.  On  fine  and  jack  fly  frames, 
all  conditions  being  good,  making  6  to  10  H.  R.,  an  allowance  of 
10  per  cent,  loss  of  time  should  be  sufficient,  on  intermediates, 
from  10  to  14  per  cent,  and  on  slubbers  from  12  to  25  per  cent., 
depending  upon  the  size  of  the  roving  being  run  and  the  length 
of  the  frame  used.  For  instance,  a  slubber  on  .4  H.  R.  will  run 
about  11  doffs  a  day,  while  the  same  slubber,  at  the  same  spindle 
speed,  would  only  run  about  4.75  doffs  per  day  on  .8  H.  R.,  con- 


FLY   FRAMES.  121 

sequently,  the  loss  of  time  due  to  doffing,  when  running  the  .4  H. 
H.  R.,  would  be  more  than  2  1/3  times  as  great  as  when  running 
the  .8  H.  R.,  and  the  percentage  of  the  total  production  obtained 
in  the  former  case  would  be  correspondingly  less.  This  is  true  on 
all  the  frames.  Some  mills  use  doffer  girls,  whose  duty  it  is  to 
help  the  tenders  doff  and  creel  their  frames,  one  girl  being  placed 
to  a  certain  number  of  frames.  Where  this  system  is  used,  the 
-percentage  of  production  is  larger. 

All  frames  are  equipped  with  a  clock  which  registers  the 
number  of  hanks  run.  The  mechanism  of  the  clock  is  run  from 
a  worm  on  the  end  of  the  front  roll  and  is  adjusted  to  the  size  of 
the  roll  so  that  it  will  register  one  hank  when  the  roll  has  made 
enough  revolutions  to  cause  it  to  deliver  840  yards  of  roving. 
The  clocks  should  be  read  at  the  same  time  every  day,  thus  show- 
ing a  record  of  each  day's  run  for  each  frame  and  operative,  giv- 
mg  a  comparison  between  the  efficiency  of  the  operatives. 

The  actual  production  of  the  frame  in  pounds  per  day  can 
be  found  by  the  following  rule: 

Multiply  the  hanks  registered  on  the  clock  by  the  number  of 
spindles  on  the  frame  and  divide  by  the  H.  R.  being  run. 

Examnle:  A  fine  frame  is  running  6  H.  R.,  the  spindle 
speed  is  1,200  R.  P.  M.,  the  twist  per  inch  is  2.92  turns,  the  front 
roll  is  I1/-  inches  in  diameter  and  is  making  116  R.  P.  M.  The 
hank  clock  registers  7.7  hanks  for  one  day's  run  and  the  frame 
has  160  spindles,  what  is  the  production  in  pounds? 

7,7X160 

=  205.33  Ibs.  per  day. 
6 

The  above  gives  a  correct  idea  of  the  production  of  the 
frame  and,  where  several  frames  of  the  same  size  ar<3  running  on 
the  same  H.  R.,  an  average  of  the  clock  readings  of  all  the  frames 
can  be  used  to  figure  the  total  production  that  is  being  turned  off, 
but  it  gives  us  no  idea  of  the  per  cent,  of  production  that  is  being 
produced.  To  do  this,  we  must  calculate  the  theoretical  produc- 
tion of  the  frame  and  compare  the  two  sets  of  figures. 

To  get  the  theoretical  production,  there  are  two  methods 
that  we  can  use : 

First:  Base  our  calculations  on  the  front  roll  speed.  This 
varies  with  every  change  in  twist  gear  and  should  be  ascertained 
before  making  the  calculation  or  the  results  will  not  be  correct. 

Second :  Base  our  calculations  on  the  speed  of  the  spindles 
and  the  twist  in  the  roving.  However,  the  SDeed  of  the  spindles 
is  often  not  what  it  is  supposed  to  be,  on  account  of  loss  of  motion 
due  to  belt  slippage,  etc. 

Taking  the  second  method  and  calculating  the  production 


122  COTTON   MILL   MACHINERY   CALCULATIONS. 

without  allowance  for  loss  of  time,  we  get  the  theoretical  produc- 
tion. Spindle  speed  divided  by  the  twist  per  inch  gives  the  inches 
delivered  per  minute:  1,200 -=- 2.92  =  410.96  inches  of  roving 
per  minute.  Multiplied  by  the  minutes  in  a  day  gives  the  inches 
delivered  in  a  day :  410.96  x  600  =  246,396  inches  per  day.  Di- 
vide this  by  36  to  get  the  yards  per  day :  246,396  H-  36  =  6,844.33 
yards.  Then  divide  the  yards  delivered  by  the  number  of  yards 
in  one  pound  of  6  H.  R.  and  it  will  give  the  pounds  produced. 

6,844.33 

=  1.358  Ibs.  produced. 

6X840 

This  amount  is  for  one  spindle  and  must  be  multiplied  by  the 
number  of  spindles  in  the  frame  to  give  the  total  theoretical  pro- 
duction of  the  frame.  Then :  1.358  x  160  =  217.28  pounds  per 
day. 

The  actual  production,  as  figured  from  the  clock  reading, 
was  205.33  pounds.  Then :  205.33  ~  217.28  =  .94  +  or  a  produc- 
tion of  a  little  over  94  per  cent.,  showing  a  loss  of  time  of  nearly 
6  per  cent. 

In  running  the  card  room,  the  theoretical  production  for  the 
whole  room  can  be  figured  and  a  comparison  made  with  the  actual 
results  obtained  from  the  clock  readings,  showing,  at  a  glance, 
the  per  cent,  of  possible  production  being  turned  off  and  giving 
an  accurate  idea  of  the  efficiency  of  the  machines  and  operatives. 

If  we  figure  the  theoretical  production  from  the  front  roll 
speed,  we  get  the  following,  the  front  roll  being  3.53  inches  in 
circumference : 

3.53X116X600X160 

=  216.65   pounds. 

36X6X840 

This  compares  closely  with  the  217.28  pounds  obtained  from 
the  former  figuring  above,  the  difference  being  explained  in  the 
handling  of  the  decimals. 

It  is  not  possible  to  work  out  a  production  constant  for  fly 
frames  that  would  be  applicable  to  any  and  all  conditions,  as  all 
the  quantities  in.  the  production  calculation  are  variable  to  a  large 
extent.  However,  assuming  the  conditions  mentioned  in  the  ex- 
ample to  be  present,  the  production  constant,  based  on  one  spin- 
dle and  no  allowances  for  loss  of  time,  would  be : 

1,200X600 

—  =  23.8. 
36X840 

If  we  divide  this  constant  by  the  product  obtained  by  multi- 
plying the  twist  per  inch  by  the  size  of  the  hank  roving,  we  will 
get  the  pounds  produced  by  one  spindle. 


FLY   FRAMES.  123 

A  production  constant  of  this  kind,  based  on  the  conditions 
as  actually  present  on  the  machines,  would  be  useful  in  determin- 
ing the  theoretical  production  on  any  number  of  frames,  for  any 
size  roving  and  give,  at  a  glance,  the  amount  of  roving  to  be  ex- 
pected from  any  given  number  of  spindles. 

In  getting  the  average  number  of  roving  or  yarn  that  is  be- 
ing produced  on  a  set  of  frames,  we  have  to  base  the  figures  on 
the  total  length  turned  out  and  the  total  pounds  produced.  The 
rule  is : 

Divide  the  total  hanks  produced  by  the  total  pounds  pro- 
duced. 

Example:  A  card  room  has  20  fine  fly  frames  of  160  spin- 
dles each;  6  frames  on  3  H.  R.,  the  clock  readings  average  9.5 
hanks  per  day ;  4  frames  on  3.50  H.  R.,  the  clock  readings  average 
9  hanks  per  day ;  7  frames  on  4.5  H.  R.,  the  clock  readings  average 
8.25  hanks  per  day;  3  frames  on  5.5  H.  R.,  the  clock  readings 
average  7.6  hanks  per  day-  What  is  the  average  H.  R.  being  run? 

6  X  160  X  9.5    =  9,120  hanks.  9,120  -=-  3     =  3,040  Ibs. 
4  X  160  X  9.      =  5,760  hanks.  5,760  -H  3.5  =  1,646  Ibs. 

7  X  160  X  8.25  =  9,240  hanks.  9,240  -r-  4.5  =  2,059  Ibs. 
3  X  160  X  7.6    =  3,648  hanks.  3,648  •*•  5.5  =     663  Ibs. 


Total  hanks  =  27,768  Total  pounds  =  7,402 

Then:     27,768-^-7,402  =  3.75  average  H.  R.  being  run. 

The  following  table  of  production  constants,  based  on  the 
speed  of  the  spindles,  are  worked  out  for  a  range  of  speeds,  based 
on  a  10  hour  day  and  no  allowance  made  for  loss  of  time.  Any 
production  figured  with  their  use  will  be  theoretical  production 
and  it  can  be  used  as  a  comparison  with  what  is  actually  obtained 
from  the  machines. 

Rule: 

Production  Constant 

=  Ibs.  per  spindle. 

Twist  x  counts. 

Production  constant  for  intermediate  speeds,  not  shown  in 
the  table,  can  be  gotten  by  proportion  or  by  multiplying  .0198  by 
the  speed  of  the  spindles. 

Example:  What  would  be  the  production  constant  on  a 
speeder  that  has  a  spindle  speed  of  1,187  R.  P:  M.?  . 

1187 X. 0198  =  23.50  production  constant. 


124 


COTTON  MILL   MACHINERY   CALCULATIONS. 


SPINDLE  SPEED 

650 

700 

750 

800 

850 

900 

950 
1,000 
1,050 
1,100 
1,150 
1,200 
1,250 
1,300 


PRODUCTION  CONSTANT 

12.87 
13.86 
14.85 
15.84 
16.83 
17.32 
18.81 
19.80 
20.79 
21.78 
22.77 
23.76 
24.75 
25.74 


The  production  of  a  fly  frame  is  often  based  on  the  speed 
of  the  front  roll.  As  the  front  roll  on  all  frames  are  not  the  same 
size,  the  following  constants  were  worked  out  to  suit  the  different 
sizes  of  rolls  that  may  be  used.  They  are  based  on  a  10  hour  day 
and  no  allowance  made  for  loss  of  time. 

Rule: 


Production  Constant  X  R-  P-  M.  of  front  roll 


Counts 


=  Ibs.     per 
spindle. 


.078  for  W  roll. 

.074  for  1  3/16"  roll. 

.070  for  li/8"  roll. 

.066  for  1  1/16"  roll. 


FLY   FRAMES. 


125 


PRODUCTION    OF   FLY   FRAMES 


Pounds  per  Day  per  Spindle 

Number 
of 
Roving 

Grains 
per 

Twist 
Inch 

Slubber 

Intermediate 

Roving 

Jack 

10  in. 

9  in. 

9  in. 

6%  in. 

6  in.      5U  in. 

\V  in 

4&  in. 

Space 

Space 

Space 

Space 

Space 

Space 

Space 

Space 

.20 

41.67 

.54 

58.71 

.30 

27,78 

.66 

41.60 

39.09 

.40 

20.83     i           .76 

31.19 

30.69 

29.36 

.60 

16.67                .85 

24.03 

24.29 

23.99 

.60           13.89               .93 

19.32 

20.05 

19.95 

.70           11.90             1.00 

15.75 

16.60 

16.92 

.80     !       10.42 

1.07          13.25 

14.13 

14.46 

1 

.90     '••        9.26 
1.00             8.33 

1.14          11.24 
1.20     i       9.83 

12.04 
10.64 

12.36 
10.97 

13.92 
12.33 

12  88 

1.10 
1.20 
1.30 
1.40 

7.57 
6.94 
6.41 
5.95 

1.26 
1.31 
1.37 
1.42 

'.'.'.'.'.'.'.'. 

10.48 

9.75 
8.70 

1L15 
10.16 
9.03 

il.75 
10.65 
9.50 
8.75 

1.60 

5.55             1.47          

7  62 

8.15 

1.60 

5.20 

1.52          

6  89 

7  64 

1.70 
2.00 

4.90 
4.16 

1.56 
1.70 

5^91 

7^19 
5.63 

5.87 

2.25 

3.70 

1.80 



4  94 

5  21 

2.50 

3.33 

1.89 

4^21 

4^45 

2.75 

3.03 

1.98 

3.72 

3^86 

3.00 
3.50 

2.77 
2.38 

2.08 
2.24 



'.'.'.'.'.'.'.'. 

3.32 

3^54 
2.93 

357 
3.06 

4.00 

2.08 

2.4Q          

2^39 

•  2^45 

4.50 

1.85 

2.54 

2  07 

2  18 

5.00 

1.67 

2.68 

1^75 

1  83 

5.50 

1,51 

2.81          

1.54 

1  67 

6.00 
7.00 

1.38 
1.19 

2.94     i     
3-17     1     



1.37 

1.43 
1.15 

8.00 

1.04 

3.39     !     

9.00 

.92 

3.60 

787 

10.00 

.83 

3-79 

•°R7K 

.822 

11.00 

.76 

3.98 

'" 

.747 

12.00 

.69 

4.16 

.622 

14.00 

.59 

4.49 



.497 

16.00 

.52 

480 



.410 

18.00 

.46 

5.09 

355 

20.00 

.42 

5.37 

.297 

22.00 

.38 

5.63 



.262 

24.00 

.35 

5-88 

.233 

26.00 

.32 

6.12 



:::::::: 

!206 

Rev.  of  Pulley  per  Minute, 

344 

391 

392 

490 

441 

423 

456 

556 

Rev.  of  Flyer  per  Minute. 

660 

750 

800 

1000 

1150 

1300 

1400 

1700 

Size  of  Full  Bobbin                  •( 

12  in. 

11  in, 

10  in. 

9  in. 

8  in. 

7  in. 

6  in. 

5  in. 

6H  in. 

5H  in 

5/8  in. 

4%  in. 

4/^  in. 

3%  in 

3/s  in. 

2%  in. 

Cotton  on  Full  Bobbin, 

46  oz. 

33  oz. 

27  oz. 

21  oz. 

16  oz. 

10%  oz. 

7%oz. 

4  oz. 

126  COTTON  MILL  MACHINERY   CALCULATIONS. 

CHAPTER  VIII. 

SPINNING — DRAFT — TWIST — SPEED — PRODUCTION — ROLL  SET- 
TING— AVERAGE  NUMBER. 

SPINNING  FRAMES. 

The  object  of  the  spinning  process  is  to  convert  one  or  two 
strands  of  roving,  by  reducing  its  size  and  adding  a  certain 
amount  of  twist,  into  a  smooth,  strong  yarn  and  putting  it  on  a 
bobbin  or  quill  of  suitable  size  for  use  on  the  machines  follow- 
ing. The  reduction  in  size  is  accomplished  by  the  action  of  three 
lines  of  steel  fluted  drawing  rolls  with  leather  covered  top  rolls 
and  the  twisting  and  winding  is  accomplished  by  the  revolutions 
of  the  .spindle  and  traveler. 

The  amount  of  draft  used  varies  greatly,  depending  upon 
the  requirements  of  the  case  and  the  ideas  of  different  individu- 
als. The  average  draft  used  can  be  stated  as  being  eight  when 
using  single  roving  and  ten  when  using  double  roving.  These 
figures  are  neither  too  high  nor  top  low  and  will,  under  most  con- 
ditions, produce  good,  even  drawing  and  give  a  smooth,  strong 
yarn. 

The  amount  of  twist  put  into  the  yarn  depends  upon  its  size 
and  the  purposes  for  which  it  is  intended.  Warp  yarn,  on  ac- 
count of  the  strength  desired,  requires  more  twist  than  filling. 
The  twist  is  based  on  the  square  root  of  the  number  or  counts  of 
the  yarn  in  all  cases.  The  different  multiples  or  multipliers  used 
depend  upon  the  requirements  of  the  different  yarns.  The  fol- 
lowing are  the  usual  multipliers  used : 

Warp  yarn,  4.75. 

Filling  yarn,  3.25. 

Doubling  yarn,  2.75. 

Hosiery  yarn,  2.50. 

The  rule  for  determining  the  amount  of  twist  is: 

Square  root  of  the  counts  x  twist  multiplier  =  tivist  p<ti 
inch. 

Following  this  rule,  the  twist  required  for  36's  warp  yan» 
would  be :  ^36  x  4.75  =  28.50  turns  per  inch. 

For  36's  filling,  the  twist  is:  V36  x  3.25-=  19.50  turns  pe^ 
inch. 

The  winding  of  the  yarn  on  the  bobbin  is  accomplished  b> 
the  drag  of  the  traveler  as  it  is  being  carried  around  the  ring  by 
the  yarn,  the  speed  of  the  traveler  deoending  upon  the  deliver} 
of  the  front  roll,  the  speed  of  the  spindle  and  the  size  of  the  bob 
bin,  its  speed  increasing  as  the  bobbin  increases  in  size. 


SPINNING   FRAMES. 


127 


The  production  of  the  frame  depends  upon  the  spindle  speed, 
the  twist  in  the  yarn  and  the  amount  of  time  consumed  by  doff- 
ing, oiling,  etc.,  and  should  be  90  per  cent,  and  over,  under  most 
conditions.  The  coarser  the  yarn,  the  more  doffing  required  ana 
the  greater  the  amount  of  time  lost. 

The  draft  gearing  of  the  majority  of  spinning  frames  is  to 
alike  in  arrangement  that  one  diagram  will  be  sufficient  for  cur 
purposes.  The  gearing  is  placed  at  either  the  head  end  or  foot 
end  of  the  frame,  the  head  end  gearing  being  the  best  arran^e- 
ment  as  it  relieves  the  tin  drum  of  the  strain  of  transmitting  tne 
power  necessary  to  drive  the  rolls  and  the  traverse  motion.  Fig. 
41  gives  a  diagram  of  the  draft  gearing  of  a  spinning  frame  bui.it 
by  the  Fales  and  Jenks  Machine  Co.,  Pawtucket,  R.  I.  The  front 


~ 


A  CAT  f*Oi-L-    -       D/A 


TO     I 


ROL-L    /    D/A. 


FIG.  41.    DRAFT  GEARING  OF  FALES  &  JENKS  SPINNING  FRAME. 

roll  is  1  inch  in  diameter  and  the  middle  and  back  rolls  are  % 
inch  in  diameter.  The  large  gear  of  108  teeth  on  the  end  of  th* 
front  roll  is  part  of  the  twist  gearing,  being  driven  from  the  cyl- 
inder shaft.  The  front  roll  gear  of  30  teeth  drives  the  cro\v:i 
gear  of  120  teeth.  On  the  stud  with  the  crown  gear  is  the  dra.t 
change  gear  which  drives  the  84  tooth  gear  on  the  back  roll.  Th;s 
gives  a  draft  constant  of: 

8X120X84 

=  384. 

SOX  X  X  7 

Constant  -f-  draft  =  gear. 
Constant  -+-.gear  =  draft. 

Then,  with  a  38  tooth  draft  gear  on,  we  would  have  the  fol- 
lowing draft :    384  -=-  38  =  10.1  draft. 


128  COTTON    MILL    MACHINERY    CALCULATIONS 

The  draft  between  the  middle  and  back  rolls,  or  back  draft, 
is  small,  being  usually  about  (1.05,  as  in  the  above  diagram. 

The  total  draft  divided  by  the  back  draft  gives  the  front 
draft :  10.1  -+- 1.05  =  9.619  front  draft. 

For  small  changes  in  the  size  of  the  yarn  the  proper  draft 
gear  can  be  found  by  calculations  similar  to  the  ones  given  on  the 
fly  frames. 

Example :  A  spinning  frame  is  making  36's  yarn  with  a  33 
tooth  draft  gear  on,  what  size  draft  gear  will  be  needed  to  give 
32's  yarn? 

Rule :  Gear  on  frame  x  counts  on  frame  -7-  counts  wanted 
=  gear  needed. 

Then :    38  x  36  -=-  32  =  42.7  or  43  tooth  draft  gear  needed. 

In  changing  the  draft  gear  from  the  weight  of  the  yarn,  the 
following  rule  holds  good: 

Gear  on  the  frame  x  weight  wanted  -5-  iveight  on  the  framt 
=  gear  needed. 

Example:  A  frame  with  a  40  tooth  draft  gear  is  delivering 
yarn  that  weighs  54  grains  per  120  yards,  what  size  gear  will 
be  needed  to  change  the  weight  to  50  grains  ? 

40  x  50  -r-  54  =  37  tooth  gear  needed. 

In  changing  the  draft  gear  from  the  draft  of  the  machine, 
the  following  rule  is  correct: 

Gear    on    frame  x  draft    on    frame  -j-  draft    desired  =  draft 
gear  needed. 

Example:  If  a  draft  gear  of  38  teeth  gives  a  draft  of  10, 
what  size  gear  will  be  needed  to  give  a  draft  of  10.75? 

38  x  10  -f-  10.75  =  35.3  or  35  tooth  gear. 

In  figuring  the  actual  draft  from  the  weight  of  material 
back  and  front,  the  following  rule  holds  true: 

Weight  on  back  x  doublings  -*-  weight  on  front  =  actual 
draft. 

In  figuring  from  the  counts  or  size,  use  the  following  rule : 

Counts  on  front  x  doublings  -f-  hanks  on  back  =  actual 
draft. 

In  dealing  with  draft  on  the  spinning  frames  a  peculiar  fact 
presents  itself,  that  is,  the  actual  draft,  as  figured  from  the  weight 
of  roving  and  yarn,  is  less  than  the  figured  draft,  as  obtained 
from  the  gearing.  This  is  explained  by  the  fact  that  while  the 
yarn  is  being  twisted,  it  contracts  in  length  and  this  contraction 
increases  its  weight,  hence,  the  roving  has  to  be  drafted  an  addi- 
tional amount  to  overcome  this  heavying  up  while  twisting.  Thus, 


.    SPINNING   FRAMES. 


129 


if  a  frame  is  spinning  30's  yarn  from  6  H.  R.  doubled,  the  actual 
draft  is :  30  x  2  -=-  6  =  10.  Now,  if  we  calculate  the  draft  from 
the  gearing,  we  will  find  it  to  be  about  10.3,  or  an  increase  of 
about  3  per  cent.,  which  is  the  amount  of  yarn  contraction  due  to 
twisting.  So  then,  any  calculation  for  draft,  made  from  the 
weight  or  size  of  the  yarn,  must  have  the  result  increased  about 
H  per  cent,  in  order  to  get  the  correct  figured  draft,  or  size  of 
draft  gear  necessary  to  put  on  the  frame.  If  the  (Jraft  is  figured 


FIG.  42.    GEARING  OF  DRAWING  ROLLS  ON  SACO-PETTEE  SPINNING 

FRAMES. 

from  the  weight  of  the  material,  the  easiest  way  of  allowing  for 
this  contraction  is  to  deduct  it  from  the « weight  of  the  finished 
yarn  on  the  front,  getting,  what  we  may  term,  the  weight  of  the 
yarn  before  twisting,  as  follows: 

30's  yarn  weighs  .2778  grs.  per  yard.     Then :     .2778  -f- 1.03 
=  .2697  grs.  before  twisting.    6  H.  R.  weighs  1.388  grs.  per  yard. 

Then:  2X1.388 

—  =  10.29  draft. 
.2697 

Fig.  42  shows  a  diagram  of  the  draft  gearing  of  the  Saco- 
Pettee  spinning  frame,  the  only  case  in  which  the  draft  gearing 
is  not  arranged  as  shown  in  Fig.  41.  The  front  roll  drives  the 
back  roll  by  a  train  of  gearing  similar  to  the  one  shown  in  Fig. 
41,  but,  instead  of  the  back  roll  driving  the  middle  roll,  the  middle 
roll  is  driven  from  the  front  roll  by  a  train  of  gearing  similar  to 
the  one  driving  the  back  roll,  being  located  at  the  opposite  end 
of  the  frame.  This  calls  for  the  use  of  two  change  gears  and 
necessitates  two  calculations  to  get  the  correct  gears  to  use. 

The  draft  constant  for  the  total  draft  is  figured  as  follows: 


8X79X84 


=  474    constant  for  total  draft. 


16X  X  X' 


130  COTTON    MILL    MACHINERY    CALCULATIONS 

Constant  -+-  draft  =  gear. 

Constant  -=-  gear  =  draft. 

By  following  the  gearing  at  the  other  end,  we  find  the  con- 
stant for  the  draft  between  the  front  and  middle  rolls,  or  front 
draft,  to  be: 

8X117X106 

—  =  472.46   constant  for  front  draft. 
SOX  X  X7 

Rule :  Constant  -5-  change  gear  on  foot  end  =  draft  be- 
tween front  and  middle  rolls. 

If  we  take  the  total  draft  and  divide  it  by  1.05,  the  amount  of 
draft  desired  between  the  middle  and  back  rolls,  we  get  the  front 
draft.  .Divide  the  constant  for  front  draft  by  the  draft  wanted 
and  we  get  the  proper  change  gear  to  use  at  this  point. 

Example:  With  above  gearing,  what  draft  gears  would  be 
necessary  to  give  a  draft  of  10.3?  Head  end  draft  gear  figured 
as  follows :  474  -j-  10.3  =  46  tooth  draft  gear. 

Foot  end  change  gear  figured  as  follows :  10.3  -=-  1.05  =  9.8 
front  draft.  472.46  -r-  9.8  =  48  tooth  foot  end  change  gear. 

In  .the  above  arrangement,  any  change  made  in  the  total 
draft,  affects  the  back  draft  and  the  break  draft  is  the  one  occur- 
ring between  the  middle  and  back  rolls. 

There  is  no  absolute  necessity  of  making  the  calculation  for 
the  foot  end  change  gear,  as  its  size  can  be  determined  from  the 
size  of  the  draft  gear,  if  we  remember  that  it  is  one  tooth  larger 
than  the  draft  gear  when  that  gear  has  45  teeth  or  less  and  two 
teelh  larger  when  the  draft  gear  has  more  than  45  teeth. 

TWIST  GEARING. 

The  twist  is  considered  as  the  ratio  between  the  delivery  of 
the  front  roll  and  the  spindle  speed.  Fig.  43  shows  the  arrange- 
ment of  the  twist  gearing  of  the  spinning  frame.  On  the  tin 
cylinder  or  drum  is  a  30  tooth  gear,  called  the  drum  or  cylinder 
gear,  which  drives  the  90  tooth  jack  or  stud  gear.  On  the  stud 
with  the  jack  gear  is  the  twist  gear  which  drives  to  the  front  roll 
gear  of  118  teeth,  using  one  intermediate  in  one  drive  and  two  in 
the  other,  thus  giving  both. drawing  rolls  motion  in  opposite  di- 
rections. The  cylinder  is  7  inches  in  diameter  and  the  whorl  of 
the  spindle  is  %  inch  in  diameter.  As  the  ratio  between  the  diam- 
eters of  the  cylinder  and  whorl  is  not  the  ratio  between  their 
speeds,  we  cannot  use  the  two  diameters,  but  have  to  use  a  ratio 
which  is  supposed  to  represent  the  number  of  revolutions  the 
spindle  makes  for  every  one  of  the  cylinder  under  workin/  con- 


SPINNING   FRAMES. 


131 


ditions.  This  ratio  is  given  as  7.25  for  the  two  diameters  used 
above  and  is  figured  so  as  to  make  necessary  allowance  for  band 
slippage,  etc. 


FIG.    43. 


GEARING    END    OF  A    SPINNING    FRAME 
ARRANGEMENT  OF  TWIST  .GEARING. 


SHOWING 


The  front  roll  is  1  inch  in  diameter  or  3-1V16  inches  in  cir- 
cumference and  the  twist  constant  is  found  as  follows,  the  calcu- 
lation being  similar  to  that  used  on  the  fly  frames  : 

118X90X7.25 

—  =  817.36  twist  constant. 
3.1416XXX30 

Putting  this  in  the  form  of  a  rule  we  get  the  following  : 
Front  roll  gear  x  jack  gear  x  ratio 


=  twist  constant. 


3.1416 


drum  gear. 


132  COTTON    MILL    MACHINERY    CALCULATIONS 

Constant  -~-  gear  =  twist. 
Constant  -f-  twist  =  gear. 

Example:  With  a  frame  geared  as  above,  what  size  twist 
gear  would  be  required  to  run  25's  warp  yarn? 

V25  =  5;   5X4.75  =  23.75  turns  of  twist: 

Then:     817.36 -e-  23.75  =  34.4  or  34  tooth  gear  required. 

By  using  different  combinations  of  jack  and  cylinder  gears 
and  different  size  front  roll  gears  almost  any  range  of  twist  de- 
sired can  be  obtained. 

In  figuring  the  twist  gear  when  changing  the  size  of  the  yarn, 
the  following  rules  will  be  found  useful  and  convenient: 

Gear  on  the  frame  x  twist  in  the  yarn  ~-  twist  wanted  = 
twist  gear  needed. 

Example:  A  frame  is  putting  in  32  turns  of  twist  with  a 
40  tooth  twist  gear  on,  what  size  gear  will  be  needed  to  reduce 
the  twist  to  24  turns? 

32X40 

—  =  53  tooth  gear  needed. 
24 

By  using  the  square  root  of  the  yarn,  the  proper  twist  gear 
can  be  determined,  without  knowing  the  amounts  of  twist,  by  the 
following  rule : 

V  Counts  on  frames  x  gear  on  frame  -f-  V  counts  wanted  = 
twist  gear  needed. 

Example:  A  frame  is  running  28's  warp  with  a  40  tooth 
twist  gear  on,  what  size  gear  will  be  needed  to  run  32's  warp  ? 

V  28  =  5.29.      V  32  =  5.66. 
5.29X40 

—  =  37.3  or  37  tooth  gear  needed. 
5.66 

Although  the  universal  custom  is  to  consider  the  speed  of 
the  spindle  as  the  basis  for  determining  the  amount  of  twist  put 
in  the  yarn,  the  statement  that  every  revolution  of  the  spindle 
puts  in  one  turn  of  twist  is  not  correct  and  the  ratio  between  the 
spindle  speed  and  the  front  roll  delivery  is  not  the  exact  twist. 
The  amount  of  twist  actually  put  into  the  yarn  depends  upon  the 
speed  of  the  traveler,  as  the  revolving  of  the  traveler  around  the 
ring  produces  the  turning  or  twisting  of  the  yarn  on  its  own  axis. 
The  traveler  speed  depends  upon  the  spindle  speed,  the  size  of  the 
bobbin  and  the  front  roll  delivery,  being  greatest  when  the  bob- 
bin is  full.  In  other  words,  the  traveler  lags  behind  the  spindle 
enough  revolutions  to  cause  the  bobbin  to  wind  up  the  yarn  de- 
livered by  the  front  roll.  Suppose  the  front  roll  to  make  120  R.. 


SPINNING  FRAMES.  133 

P.  M.,  the  spindle  speed  to  be  9,500  R.  P.  M.,  and  the  diameter  of 
the  bobbin  to  be  %  inch.  Now,  while  the  bobbin  and  spindle  go 
at  the  same  speed,  the  traveler  lags  behind.  The  front  roll  deliv- 
ers :  120  x  3.1416  =  376.99  inches  of  yarn  per  minute.  Allow- 
ing for  the  3  per  cent,  contraction  in  twisting,  then  the  length  of 
yarn  actually  delivered  to  and  wound  on  the  bobbin  is :  376.99  x 
.97  =  365.68  inches. 

The  bobbin  is  %  inch  in  diameter  or  2.75  inches  in  circum- 
ference, then,  for  every  revolution  that  the  traveler  lags  behind, 
the  bobbin  will  wind  on  2.75  inches  of  yarn  and,  to  wind  on  the 
total  delivery  of  the  front  roll,  the  traveler  will  have  to  lag  be- 
hind :  365.68  -r-  2.75  =  133  revolutions. 

Then,  9,500  — 133  =  9,367  R.  P.  M.  as  the  speed  of  the  trav- 
eler. Divide  the  traveler  speed  by  the  front;  roll  delivery  and  we 
get  the  actual  amount  of  twist  that  is  being  put  into  the  yarn,  as 
follows : 

9367  -5-  365.68  =  25.61  turns  per  inch. 

If  the  twist  is  based  on  the  spindle  speed,  it  works  out  as  fol- 
lows: 

9500  -T-  365.68  =  25.97  turns  per  inch. 

This  shows  very  little  variation  from  the  correct  conditions 
and  is  not  of  enough  importance  to  be  considered.  Ordinarily 
the  twist  calculation  is  based  on  the  front  roll  surface  speed  and 
the  spindle  speed,  no  allowances  for  yarn  contraction  or  the  lag 
of  the  traveler  being  taken  into  consideration  and  the  result  is 
accurate  enough  for  every  purpose.  In  the  above  case,  the  spindle 
speed  divided  by  the  surface  speed  or  delivery  of  the  front  roll, 
will  give  25.19  turns  of  twist  per  inch,  not  enough  variation  to  be 
noticed. 

Although,  on  most  frames,  there  is  a  traverse  gear,  which 
regulates  the  speed  of  the  ring  rail  and  is  changed  when  making 
wide  variations  in  the  size  of  the  yarn,  there  is  no  calculation 
necessary  to  determine  its  size,  it  being  simply  a  matter  of  judg- 
ment based  upon  the  way  the  yarn  lays  on  the  empty  bobbin. 

PRODUCTION. 

As  on  the  fly  frame,  the  production  of  a  spinning  frame  can 
be  figured  from  the  spindle  or  front  roll  speed.  Either  will  give 
good  results. 

Example :  What  is  the  production  of  a  frame  of  256  spindles 
on  28's  yarn,  warp  twist,  if  the  spindle  speed  is  9,500  R.  P.  M., 
allowing  a  loss  of  time  of  10  per  cent. :  V28  X  4.75  ==  25.13  turns 
of  twist.  .. 


134  COTTON    MILL    MACHINERY    CALCULATIONS 

9500X600X256X.90 


61.72  Ibs.   per   day. 


25.13X36X28X840 

The  above  calculation  can  be  made  for  one  spindle,  by  leav- 
ing out  the  256,  and  this  result  multiplied  by  the  number  of  spin- 
dles will  give  the  total  production. 

The  finer  the  yarn  run,  the  fewer  times  the  frame  is  doffed 
and  the  less  the  loss  of  time,  so,  in  coarse  yarns  we  can  look  for 
less  production,  as  compared  with  the  theoretical  production, 
than  when  running  the  finer  numbers  of  yarn. 

A  production  constant  can  be  worked  out,  from  the  data 
given  in  the  above  example,  based  on  one  spindle  and  no  allowance 
for  loss  of  time,  as  follows : 

9500X600 

=  188.5  production  constant. 

36X840 

The  above  constant  is  worked  out  for  full  time  and  a  spindle 
speed  of  9,t>00  K.  P.  M.,  for  a  10  hour  day  and  is  applicable  under 
no  other  conditions.  However  one  can  be  worked  out  for  any 
spindle  speed  and  length  of  day  and,  unless  the  loss  of  time,  due 
to  doffing,  etc.,  is  allowed  for,  will  give  the  theoretical  production, 
or  the  amount  that  would  be  produced  in  that  time  if  the  frame 
was  run  continually  with  no  stops. 

Rule  for  using  constant: 

Constant  -r-  Twist  per  inch  x  counts  of  yarn  =  Ibs.  per 
spindle. 

By  multiplying  the  spindle  speed  by  .0198  the  production 
constant  for  any  spindle  speed  can  be  gotten  for  full  time. 

Example:  What  would  be  the  production  constant  for  full 
Lime  if  the  spindle  Speed  was  8,600  R.  P.  M.? 

8,600  X  .0198  =  170.28  production  constant. 

If  it  is  desired  to  figure  the  production  from  the  front  roll, 
it  can  be  done  by  using  the  following  formula,  the  1  inch  front 
roll  being  3.1416  inches  in  circumference? 

3.1416  x  R.  p.  M.  of  front  roll  x  minutes  run. 

=  Ibs.    per 

36  X  Counts  X  840  spindle. 

The  production  constant  of  .0623,  is  based  on  a  10  hour  day 
nnd  no  allowance  for  loss  of  time. 
Rule: 

Production  constant  x  R.  p,  M.  of  front  roll 

—  =  Ibs.     per 
Counts  of  yarn  spindle. 


SPINNING   FRAMES.  135 

ROLL  SETTING. 

As  a  general  rule  the  rolls  of  a  spinning  frame  can  be  set 
closer  than  those  on  a  fly  frame,  but  no  fixed  rule  can  be  given  and 
the  final  decision  must  rest  upon  the  appearance  of  the  stock  as  it 
leaves  the  rolls.  A  great  deal  depends  upon  the  condition  of  the 
stock,  the  feel  of  the  fibers,  the  draft  and  speed  of  the  rolls. 

Distance  betiveen  front  and  middle  rolls  should  be  1/16  to  % 
inch  greater  than  the  length  of  the  staple  used. 

Between  middle  and  back  rolls,  %  to  y&  inch. 

AVERAGE   NUMBER. 

In  a  spinning  room  or  mill,  where  several  sizes  of  yarn  are 
being  run,  it  is  often  desired  to  know  what  is  the  average  counts 
turned  out.  Although  it  is  figured  by  several  methods,  there 
is  only  one  that  will  give  the  correct  results  and  it .  is  based 
on  the  pounds  produced.  Any  calculation  based  on  any  other  basis 
is  wrong.  The  following  rule  and  example  will  illustrate  and  ex- 
plain the  method : 

Rule :  Divide  the  total  hanks  spun  by  the  total  pounds  spun. 
Answer  will  be  the  average  number  of  yarn  spun. 

Example:  A  mill  produces  2,500  Ibs.  of  30's,  3,000  Ibs.  of 
36's,  5,000  Ibs.  of  40's,  8,000  Ibs.  of  50's  and  2,000  Ibs.  of  60's  in 
one  week,  what  is  the  average  number  run? 

2,500X30=  75,000  hanks  of  30's 
3,000X36  =  108,000  hanks  of  36's 
5,000X40  =  200,000  hanks  of  40's 
8,000X50  =  400,000  hanks  of  50's 
2,000X60  =  120,000  hanks  of  60's 


20,500  903,000 

By  applying  the  above  rule: 

903,000  -f-  20,500  =  44.05   average   number. 


136 


COTTON    MILL    MACHINERY    CALCULATIONS 


TABLE  FOR  NUMBERING  YARN  BY  GRAINS 


Number  of 
Yarn 

si 

'ga 

Number  of, 
\arn 

M 

i! 

Number  of 
*arn 

|j 

•3 
1 

il 

jl 

M 

11 
"I 

\v 

si 

•gw 

9 

777.771 

20%|344.44||  31% 

224.08  1    42%(165.68(|53%|131.45||     77 

90.90 

9% 

756.75' 

20%|341.46||  31% 

222.221)   42y,|164.70| 

53%|130.84 

78 

89.70 

9% 

736  84, 

20% 

337.34|(  31% 

220.47  I   42%|163.74| 

53% 

130.23 

79 

88.60 

9% 

720.51 

21 

333.33||  32 

218.75 

43     |162.79((54 

129.62 

80 

87.50 

10 

700.00 

21% 

329.41     32% 

217.05 

43%|161.84|  54% 

129.03 

81     > 

86.40 

10% 

682.92J 

2iy2 

325.58  |  32%    215.38j|    43%|160.91||54%t|128.44 

82 

85.40 

10%|666.66|(21% 

321.83||  32341  213.74 

43%(160.00||54%|127.85 

83 

84.30 

10%|651.16||22 

318.18||  33 

212.12 

44     |159.09||55     |127.27 

84 

83.30 

11     |636.|36|22% 

314.60JJ  33% 

210.52  j    44%jl58.19jj55% 

126.69 

85 

82.40 

11% 

622.22)  (22% 

311.11(1  33% 

208.95 

44%  157.41  55%' 

126.12 

86 

81.40 

11% 

608.69 

22% 

307.69 

33% 

207.40  |    44%|156.42i|55%f 

125.56||     87 

80.40 

11%)595.74 

23 

3.04.34) 

34     . 

205.88]     45     |155.55||56 

125.00|     88 

79.50 

12     |583.33)|23% 

301.07)1  34% 

204.301)    45%|154.69(|56% 

124.49(|     89 

78.60 

12%|571.42||23%|297.87| 

34% 

202.89||    45%|153.84||56%|12389||     90 

77.80 

12% 

560.00II23%|294.73( 

34% 

201.43| 

453/4|152.95[|56%|123.34)|     91 

76.90 

12% 

549.01(124 

291.661 

35 

200.00 

46     |152.17||57     |122.80||     92 

76.10 

13 

546.15||24% 

288.651 

35%|  198.58 

46%|151.30|(57%|122.27||     93 

75.30 

13%|526.11| 
13%  |518.51 

24%(285.71| 
24%  282.82( 

35%|  197.32(i    46%|150.53| 
35%|  195.80      4634(149.73 

57%  121.73  1)     94     |     74.50 
57%|121.21(|     95          73.70 

13%  509.09 

25      280.00  1  36 

19444(1    47     |14893||58 

120.68(1     96 

72.90 

14     (500.00  (25%  |277.22| 

36% 

193.10|(    47%  (148.14 

58% 

120.17|     97 

72.30 

14%  491.22  25%  274.601    36% 

191.78(1    47%|147.34 

58% 

119.65(1     98 

71.40 

14%  482.76  26%  271.84  1  36% 

190.471    47%|146.59||58% 

119.14|     99 

70.70 

14%|474.57||26      269.23 

37        189.1811    48      145.83  59      118.471    100 

70.00 

15     (466  ,66|26%;  266.66  |  37%|  187.91I|    48%|146.07j|69%|118.14jj  105 

66.70 

15%|459.01|26%|264.15 

37%|  186.66(1    48%' 

144.32) 

59%|117.64  (  110 

63.60 

15%  451.61||26%|261.68|i  37%'|   185.42|j    48% 

143.58| 

59%|117.15||  115 

60.90 

15%|444.44||27      259.25 

38        184.21(1    49 

142.85||60     (116.66(1  120 

58.30 

16     |437.50  |27% 

256.88(1  38%|  183.00     49% 

142.13||61     (114.80     125 

56.00 

16%|430.76()27% 

254.54J)  38%    181.81||    49% 

141.41  62      112.90     130 

53.80 

16%|424.24||27%  |252.52( 

38%|  180.63]i    49%|140.70||63     (111.1011  135 

51.80 

16%  417.91  M 

250.00( 

39        179.48(1    50     (140  00| 

64     (109.30 

140 

50.00 

17     J411.76  28% 

247.78(1  39%  |   178.34 

50%  |139.30| 

65     (107.70 

145          48.30 

17%|405.79  |28%|245.61(|  39%|  177.2111    50%'|138.61||66     |106.10||  150 

46.70 

17%  400.00||28%  243.461 

39%|  176.10 

50%|137.93||67     |104.40(|  155 

45.20 

17%|394.36(|29     |241.37| 

40        175.00(1    51     (137.29(168 

102.90(1  160          43.80 

18      388  88-  29%|239.31]i  40%    173.91(1    51%jl36.58j|69 

101.40  |  165          42.40 

18%|383.56|I29%1237.28I|  40%|  172.83 

51%:|135.92||70     (100.00(1  170 

41.20 

18% 

378.37|(29%|235.29|)  40%)  171.77 

51%  135.26(71 

98.60H  175 

40.00 

18% 

373.33 

(30     I233,33(|  41     |  170.73!)    52 

134.61W72 

97.20(|  180          38.90 

19     (368.42 

30%231.40|  41%|  169.69(1    52%il33.97||73 

95.90(1  185          37.80 

19%|363.63  |30%(229.50||  41%    168.67|[    52y,ll33.33||74 

94.60 

190          36.80 

19%|358.97  (30%  22764(|  41%|  167.66||    52%  132.70||75        93.30 

195 

35.90 

19%|354  43(131     <|225.80!|  42 

166.66 

!    53     (132.07||76        92.10 

200 

35.00 

20     |350.00||         |            1) 

SPINNING   FRAMES. 


137 


TWIST  TABLE 


•s 

II 

53 

I1 

si1 

tf 

CO 

I 

Whitman's 
Warp 

Twist 

Extra  Mule 
Twist 

I 

Mule  Warp 
Twist 

i 
f 

boH 
I 

1 

Doubling 
Twist 

Hosiery 
Twist 

1 

1.0000        5.00 

475 

4.50 

4^00 

3.75        3.25        2.75  | 

2.50 

2 

1.4142        7.07 

6.72 

6.36 

5.66 

5.30 

4.60 

3.89 

3.54 

3 

1.7321        8  66 

8.23 

7.79 

6.93 

6.50 

5.63 

4.76 

4.33 

4 

2.0000      10.00 

9.50 

9.00 

8.00 

7.50        6.50 

5.50 

5.00 

5 

2.2361       11.18 

10.62 

10.06 

8.94 

8.39        7.27 

6.15 

5.59 

6 

2.4495      12.25 

11.64 

11.02 

9.80 

9  19        7.96 

6.74 

6.12 

7 

2.6458      13.23 

12.57 

11.91 

10.58 

9.92        8,60 

7.28 

6.61 

8 

2.8284      14.14 

13.43 

12.73 

11.31 

10.61 

9.19 

7.78 

7.07 

9 

3.0000 

15.00 

1425 

13.50 

12.00 

11.25 

9.75 

8.25 

7.50 

10 

3.1623 

15.81 

15.02 

14.30 

12.65 

11.86 

10.28 

8.70 

'    7.91 

11 

3.3166 

16.58 

15.75 

14.92 

13.27 

12.44      10.78 

•912 

8.29 

12 

3.4641 

17.32 

16.45 

15.59      13.86 

12.99      11.26 

9.53 

8.66 

13 

3.6056 

18.03 

1713 

16.23      14.42 

13.52      11.72 

9.92 

9.01 

14 

3.7417 

18.71 

17.77 

16.84      14.97 

14.03      12.16 

10.29 

9.35 

15 

3.8730 

19.36 

18.40 

17.43      15.49 

14.52 

12.59 

10.65 

9.68 

16 

4.0000 

20.00 

19.00 

18.00 

16.00 

15.00 

13.00 

11.00 

10.00 

17 

4.1231 

20.62 

19.58 

18.55 

16.49 

15.46      13.40 

1134 

10.31 

18 

4.2426 

21.21 

20.15 

19.09 

16.97 

15.91      13.79 

11.67 

10.61 

19 

4.3589 

21.79 

20.70 

19.61 

17.44 

16.35 

14.17 

11.99 

10.90 

20 

4.4721 

22.36 

21.24 

20.12 

17.89 

16.77 

14.53 

12.30 

11.18 

21 

4.5826 

22.91 

21.77 

20.62 

18.33 

17  18      14.89 

12.60 

22 

4.6904 

23.45 

22.28 

21.11 

18.76 

17.59      15.24 

12.90 

23 

4.7958      23.98 

22.78 

21.58 

19.18 

17.98 

15.59 

13.19 

24 

4.8990 

24.49 

2327 

22.05 

1960 

18.37 

15.92 

13.47 

25 

5.0000 

25.00 

23.75 

22.50 

20.00 

18.75      16.25 

13.75 

26 

5.0990 

25.50 

24.22 

22.95 

20.40 

19.12      16.57 

14.02 

27 

5.1962 

25.98 

24.68 

23.38 

20.78 

19.49 

16.89 

14.29 

28 

5.2915 

26.46 

25.13 

23.81  i|  21.17 

19.84 

17.20      14.55  ' 

29 

5.3852 

26.93 

25.58 

24.23  |  21.54 

2019      17.50      14.81 

30 

5.4772 

27.39 

26.02 

24.65      21.91 

20.54      17.80 

15.06 

31 

5.5678 

27.84 

26.45 

25.04      22.27 

20.88      18.10 

15.31 

32 

5.6569 

28.28 

2687 

25.46      22.63 

21.21      18.38 

15.56 

33 

5.7446 

28.72 

27.29 

25.85 

22.98 

21.54      18.67 

1580 

34 

5.8310 

29.15 

27.70 

26.24 

23.32 

21.87      18.95      16.03 

35 

5.9161 

29.58 

28.10 

26.62      23.66 

22.19      19.23      16.27 

36 

6.0000 

30.00 

28.50 

27.00 

24.00 

22  50      19.50      16.50 

37 

6.0828 

30.41 

2889 

27.37 

24.33 

22.81      19.77 

16.73 

38 

6.1644 

30.82 

29.28 

27.74      24.66 

23.12      20.03 

16.95 

39 

6.2450 

31.22 

29.66 

28.10      24.98 

23.42      20.30      17.17 

40 

6.3246 

31.62 

30.04 

28.46      25.30 

23.72      20.55      17.39 

41 

6.4031 

32.02 

3041 

28.81      25.61 

24.01      20.81      17.61 

42 

6.4807 

32.40 

30.78 

29.16      25.92 

24.30      21.06      17.82  \ 

43 

6.5574 

32.79 

31.15 

29.51 

26.23 

2459      21.31      18.03 

44 

6.6332 

33.17 

31.51 

29.85 

26.53 

24.87 

21.56  |  18.24 

45 

6.7082 

33.54 

31.86 

30.19    .26.83 

25.16 

21.80      18.45 

138 


COTTON    MILL    MACHINERY    CALCULATIONS 


TWIST  TABLE- Continued 


Number 
of  Yarn 

Square  Root 

Warp  Twist 

Whitman's 
Warp  Twist 

Extra  Mule 
Twist 

el 
£ 

o 

i 

Filling  Twist 

Doubling 
Twist 

46 

6.7823 

32.21 

30.52 

27.13 

25.43 

22.04 

18.65 

47 

6.8557 

32.56 

30.85 

27.42     ' 

2571 

22.28 

18.85 

48 

6.9282 

32.91 

31.18 

27.71 

25.98 

22.52 

19.05 

49 

7.0000 

33.25 

31.50 

28.00 

26.25 

22.75 

19.25 

50 

7.0711 

33.59 

31.82 

28.28 

26.52 

22.98 

19.45 

51 

7.1414 

33.92 

32.14 

2857 

26.78 

23.21 

19.64 

52 

7.2111 

34.25 

32.45 

28.84 

27.04 

23.44 

19.83 

53 

.   7.2801 

34.58 

32.76 

29.12 

27.30 

23.66 

20.02 

54 

1  7.3485 

34.90 

33.07     | 

29.39 

27.56 

23.88 

2021 

55 

7.4162 

..35.23 

33.37 

29.66 

27.81 

24.10 

20.39 

56 

.7.4833 

35.55 

33.67 

29.93 

28.06 

24  32     ' 

20.58 

57 

7.5498 

35.86 

33.97 

30.20 

28.31 

24.54 

20.76 

58 

7.6158 

36.17 

34.27 

30.46 

28.56 

24.75 

20.94 

59 

7.6811 

36.49 

34.56 

30.72 

28.80 

24.96 

21.12 

60 

7.7460 

36.79 

34.86 

30.98 

29.05 

25.17 

21.30 

61 

7.8102 

37.10 

35.15 

31.24 

29.29 

25.38 

21.48 

62 

7.8740 

37.40 

35.43 

31.50 

29.53 

25.59 

21.65 

63 

7.9373 

37.70 

35.72 

31.75 

29.76 

2580 

21.83 

64 

8.0000 

38.00 

36.00 

32.00 

30.00 

26.00 

22.00 

65 

8.0623 

38.30 

36.28 

32.25 

30.23 

26.20 

22.17 

66 

8.1240 

38.59 

36.56 

32.50 

30.47 

26.40 

22.34 

67 

8.1854 

38.88 

36.83 

32.74 

30.69 

26.60 

22.51 

68 

8  «462 

39.17 

37.11 

32.98 

30.92 

26.80 

22.68 

69 

8.3066 

39.46 

37.38 

3323 

31.15 

27.00 

22.84 

70 

8.3666 

39.74 

37.65 

33.47 

31.37 

27.19 

23.01 

71 

8.4261 

40.02 

37.92 

33.70 

31.60 

27.38 

23.17 

72 

8.4853 

40.30 

38.18 

33.94 

31.82 

27.58 

23.23 

73 

8.5440 

40.58 

38.45 

34.18 

32.04 

2777 

23.50 

74 

8.6023 

40.86 

3871 

34.41 

32.26 

27.96 

23.66 

75 

8.6603 

41.14 

38.97 

34.64 

32.48 

28.15 

23.82 

76 

8.7178 

41.41 

39.23 

34.87 

32.69 

28.33 

23.97 

77 

8.7750 

41.68 

39.49 

35.10 

32.91 

28.52 

24.13 

78 

8.8318 

41.95 

39.74 

3533 

33.12 

28.70 

24.29 

79 

8.8882 

42.22 

40.00 

35.55 

33.33 

28.87 

24.44 

80 

8.9443 

42.48 

40.25 

35.78 

33.54 

29.07 

24.60 

82 

9.0554 

43.01 

40.75 

36.22 

33.96 

29.43 

24.90 

84 

9.1652 

43.53 

41.24 

36.66 

34.37 

29.79 

25.20 

86 

9.2736 

44.05 

41.73 

37.09 

34.78 

3014 

25.50 

88 

9.3808 

44.56 

42.21 

37.52 

35.18 

30.49 

25.80 

90 

..9.4868 

45.06 

42.69 

37.95 

35.58 

30.83 

26.09 

92     . 

9.5917 

45.56 

4316 

38.37 

35.97 

31.17 

26.38 

94 

9.6954 

46.05 

43.63 

38.78 

36.36 

31.51 

26.66 

96 

9.7980 

46.54 

44.09 

3919 

36.74 

31.84 

26.94 

98 

9.8995 

47.02 

44.55 

39.60 

37.12 

!     32.17 

27.22 

100 

10.0000 

47.50 

i    45.00 

40.00 

37.50 

32.50 

27.50 

SPhVNING. 


PRODUCTION  TABLE  OF  RING  FILLING  YARN. 
FRONT  ROLL  1  INCH  IN  DIAMETER. 


jj 

d 

, 

J 

"o  t 

"o  ^ 

2 

.5*0 

.5*3 

.S'o 

d 

'S 

3 

o 

<«H        . 

a 

Ifl     £V 

a* 

a^ 

S1^ 

£ 
» 

o 

fc 

•5, 

'o 
ij 

•a 

ii 

•3 

It 

11 

Twist  per  i 

|l| 

I8^' 

II1 

CH 

1 

T3 

"  4>  £ 

2-UJ 

1i« 

&* 

MI 

t- 

Ml 

Is 

13- 

4 

6.50 

240 

5000 

10.00 

14.40 

14.88 

16.37 

5 

7.27 

230 

5400 

10.00 

11.50 

11.95 

13.15 

6 

7.9C 

220 

5600 

9.85 

9.53 

9.86 

10.84 

7 

O 

8.60 

214 

5800 

9.85 

8.13 

8.40 

9.24 

8 

f 

9.19 

208 

6000 

9.75 

7.07 

7.31 

8.04 

9 

* 

9.75 

202 

6200 

9.65 

6.24 

6.46 

7.10 

1O 

*-. 

10.28 

196 

6400 

9.60 

5.56 

5.76 

6.33 

11 

10  18 

190 

6t>UO 

9.50 

5.00 

5.18 

5.70 

12 

• 



11.26 

184 

6600 

9.40 

4.54 

4.70 

5.17 

13 

r^ 

11.72 

180 

6700 

9.35 

4.15 

4.29 

4.72 

14 

Q 

12.16 

176 

C800 

9.25 

3.82 

3.95 

4.35 

15 

** 

12.59 

172 

6900 

9.15 

3.53 

3.65 

4.02 

16 

^N 

13. 

108 

7000 

9.05 

3.28 

3.39 

3.73 

17 

I~l 

13.40 

166 

7100 

9.00 

3.07 

3.17 

3.48 

18 

13.79 

162 

7200 

8.80 

2.84 

2.93 

3.22 

19 

« 

14.17 

158 

7200 

8.70 

2.64 

2.74 

3.02 

2O 

14.53 

156 

7300 

8.60 

2.49 

2.58 

2.83 

21 

14.89 

154 

7300 

8.50 

2.34 

2.42 

2.67 

22 

15.24 

•   152 

7400 

8.40 

2.21 

2.29 

2.52 

23 

15.59 

150 

7400 

8.30 

2.09 

2.16 

2.38 

24 

15.92 

148 

7600 

8.20 

1.98 

2.05 

2.25 

25 





16.25 

146 

7000 

8.10 

1.87 

1.94 

2.13 

36 

§ 

17.84 

144 

8000 

7.95 

1.77 

1.83 

2.01 

27 

| 

18.19 

142 

8200 

7.85 

1.68 

1.74 

1.91 

28 

en 

18.52 

140 

8200 

7.75 

1.60 

1.66 

1.83 

29 

18.84 

138 

8300 

7.60 

1.52 

1.57 

1.73 

30 

£ 

CO 

19.17 

136 

8300 

7.55 

1.45 

1.51 

1.66 

31 

£5 

20.88 

134 

8sOO 

7.45 

1.39 

1.44 

1.58 

32 

<2 

^ 

\» 

21.21 

132 

8800 

7.35 

1.33 

1.38 

1.52 

33 

oT 

"c3 

«M 

21.54 

130 

8900 

7.25 

1.27 

1.31 

1.44 

34 



21.87 

128 

8900 

7.20 

1.22 

1.27 

1.39 

35 

o 

22.19 

126 

8900 

7.10 

1.17 

1.21 

1.33 

•& 

\.j 

22.50 

124 

8900 

7.00 

1.12 

1.16 

1.28 

37 

14 

cs 

22.81 

122 

8800 

6.90 

1.08 

1.11 

1.23 

38 

~. 

23.12 

120 

8800 

6.80 

1.03 

1.07 

1.18 

39 

E 

Q 

23.42 

118 

8800 

6.70 

.99 

1.03 

1.13 

40 



23.72 

116 

8800 

6.65 

.96 

1.00 

1.10 

41 

24.01 

114 

8700 

6.55 

.92 

.96 

1.06 

42 

-\ 

24.30 

112 

8700 

6.40 

.88 

.91 

1.00 

43 

10 

24.59 

110 

8600 

6.30 

.84 

.87 

.96 

44 

24.87 

108 

8600 

6.20 

.81 

.84 

.93 

45 

25  16 

106 

8500 

6.10 

.78 

.81 

.89 

46 

25.43 

104 

8500 

6. 

.75 

.78 

.86 

47 

25.71 

104 

8500 

6. 

.74 

.76 

.84 

48 

25.98 

102 

8400 

5.90 

.71 

.73 

.81 

49 

26.25 

102 

8300 

5.90 

.69 

.72 

.79 

5O 

^ 



26.52 

100 

8200 

5.80 

.67 

.69 

.76 

55 

*""* 

27.00 

96 

8200 

5.50 

.60 

'66 

60 

2700 

92 

8000 

5.30 

.51 

.53 

.58 

65 

27.00 

88 

7700 

5.10 

.45 

.47 

.52 

70 

27.19 

84 

7400 

4.90 

.40 

.42 

.47 

75 

28.15 

82 

7400 

4.80 

.37 

.38 

.42 

80 

lO 

29.07 

80 

7400 

4.60 

.33 

34 

.37 

85 

29.96 

78 

.7400 

4.60 

.31 

.32 

.35 

90 

31.00 

76 

7400 

4.40 

.28 

.29 

.32 

95 

31.68 

74 

7400 

4.40 

.26 

.27 

.30 

100 

32.50 

72 

7400 

4.30 

.24 

.25 

.28 

SPINNING. 


PRODUCTION  TABLE  OF  RING  WARP  YARN. 
FRONT  ROLL  1  INCH  IN  DIAMETER. 


>fYarn.  1 

I 

3  of  frame.  1 

0 

L 

s| 

ll 

| 

**, 

•  25.  • 

.2~  '3 

utions  of  1 
die  per 
inute. 

uj 

S-* 

fig 

!M 

.5*3 

I* 

H\ 

0 

o' 

M 

-  *" 

3 

3  2 

| 

1|  ^ 

"5.5  S 
>  n. 

c.S"o 

las 

|*1 

"c  =-2 

* 

I 

£ 

tf* 

0    (/) 

m 

~     -g 

£3° 

£^ 

£^ 

4 

. 

9.50 

204 

6200 

10.50 

15.22 

15.75 

17.32 

5 

10  02 

200 

6800 

10.40 

12.06 

12.48 

13.72 

G 

1  1  .64 

196 

7300 

10.30 

9.95 

10.30 

11.33 

7 

g? 

12.57 

192 

7700 

10.20 

8.45 

8.74 

9.61 

8 

8 

13.44 

188 

8100 

10.10 

7.32 

7.57 

8.33 

9 

,2 

14.25 

184 

8400 

10.00 

6.44 

6.66 

7.33 

10 

;| 

m 



g 

15.02 

180 

8600 

9.80 

5.68 

5.88 

6.46 

11 

. 

c 

15.75 

176 

8800 

9.60 

5.06 

5.23 

5.76 

12 

| 

NP 

£ 

16.45 

172 

9000 

9.40 

4.54 

4.70 

5.17 

13 

at 

Jr 

17.13 

168 

9000 

9.20 

4.10 

4.24 

4.67 

14 

(5 

t* 

17.77 

164 

9000 

9.00 

3  72 

3.85 

4.24 

15 

18.40 

160 

9300 

8.80 

3.40 

3.52 

3.86 

16 

19. 

156 

9400 

8.00 

3.11 

3.22 

3.54 

17 

ID.  58 

152 

9400 

8.40 

2.86 

2.96 

3.26 

18 

20.15 

148 

9400 

8.20 

2.64 

2.73 

3.00 

19 

20.71 

144 

9400 

8.00 

2.44 

2.52 

2.77 

20 



21.24 

140 

9400 

7.80 

2.26 

2.34 

2.57 

21 

21.77 

138 

9400 

7.70 

212 

2.20 

2.42 

22.28 

136 

SI500 

7.60 

2.00 

2.07 

2.28 

23 

22.78 

134 

9000 

7.50 

1.89 

1.95 

2.15 

24 

23.27 

132 

9600 

7.40 

1.78 

1.85 

2.03 

25 

~*~' 

23.75 

13*0 

9600 

7.30 

1.69 

1.75 

1.92 

26 

24.22 

128 

9700 

7.20 

1.60 

1.66 

1.82 

27 

24.68 

126 

9700 

7.10 

1.52 

1.57 

1.73 

28 

25.13 

124 

9700 

7.00 

1.45 

1.50 

1.65 

29 

^J 

25.58 

122 

9800 

6.90 

1.38 

1.42 

1.57 

30 

26.02 

120 

9800 

6.80 

1.31 

1.36 

1.49 

31 

26.45 

120 

9900 

6.80 

1.27 

1.31 

1.44 

32 

SM 

26.87 

118 

10000 

6.70 

1.21 

1.25 

1.38 

33 

W 

27.29 

118 

10100 

6.70 

1.17 

1.21 

1.34 

34 

27-70 

116 

10200 

6.60 

1.12 

1.16 

.'28 

35 

28.10 

116 

10300 

6.60 

1.09 

1.18 

.'24 

36 

• 

28.17 

114 

10200 

6.50 

1.04 

1.08 

.19 

37 

oj 

SR 

28.24 

114 

10100 

6.50 

1.01 

1.05 

.15 

38 

g 

28.31 

112 

10000 

6.40 

.97 

1.01 

.11 

39 

o 
y. 

_C 

1 

28.38 

112 

10000 

6.40 

.95 

.98 

1.08 

40 

o> 

\* 

28.46 

110 

10000 

6.30 

.91 

.94 

1.03 

41 

9 

It 

~-" 

*™~~ 

28.81 

110 

10000 

6.30 

.89 

.92 

1.01 

42 

ft 

29.16 

108 

10000 

6.20 

.85 

.88 

.97 

43 

29.50 

108 

10000 

6.20 

.83 

.95 

44 

29.1,5 

106 

10000 

6.10 

.80 

.83 

.91 

45 

30.19 

106 

10000 

6.10 

.78 

.81 

.89 

46 

30.51 

104 

10000 

6. 

.75 

.78 

.86 

47 

H£! 

<D 

30.85 

104 

10000 

6. 

.74 

.76 

.84 

48 

31.18 

102 

10000 

5.90 

.71  • 

.73 

.81 

49 

31.50 

102 

10000 

5.90 

.69 

.72 

.79 

50 

31.81 

100 

10000 

5.80 

.67 

.69 

.76 

55 

33.37 

96 

10000 

5.60 

.59 

.61 

.67 

60 

34.86 

92 

10000 

5.40 

.62 

.54 

.59 

65 

~ 

36.28 

88 

10000 

5.20 

.46 

.48 

.52 

70 

37.65 

84 

10000 

5. 

.41 

.42 

.47 

75 

38.97 

80 

9800 

4.80 

.37 

.38 

.42 

80 

~£ 

39.08 

78 

9600 

4.70 

.34 

.35 

.38 

85 

39.18 

76 

9400 

4.60 

.31 

.32 

.35 

90 

«°! 

•*-> 

40.32 

74 

9400 

4.50 

.29 

.30 

.33 

95 

*° 

41.22 

72 

9400 

4.35 

.26 

.27 

.30 

J.OO 

42.50 

70 

9400 

4.20 

.24 

25 

.27 

SPINNING   FRAMES. 


141 


TRAVELLER  TABLE 
For  Whitin  Ring  Spinning  Frames  with  Separators. 


Warp  Yarn 

Filling  Yarn 

Number  of 
Yarn 

Revolutions 
of  Spindles 

Diameter  of 
Ring 

Number  of 
Traveller 

Weight  of  10 
Travellers 
in  grains 

Number  of 
Yarn 

Revolutions 
of  Spindles 

Diameter  of 
Ring 

Number  of 
Traveller 

Weight  of  10 
Travellers 
in  grains 

4 

4950 

2" 

14 

39       4  ||  4000 

1%" 

16    44 

6 

5900 

12 

33 

6  ' 

4800 

13    36 

8  '|f  6700 

9 

23 

• 

5450  | 

10    26 

10  ||  7250 

8 

20 

10  • 

5950 

8    20 

11  1  7500 

7 

18      11 

6150 

7  ' 

18 

12  ||  7750 

6 

16      12  '|  6350 

6 

16 

13    7950 

6 

16 

13  ||  6500 

5 

14 

14    8100 

5 

14 

14  |  6700 

4     13 

15  ||  8300 

4 

13 

15  ||  6850 

3 

12 

16 

8450 

3 

12 

16 

6950 

2    11 

17 

8600 

2 

11 

17 

7100 

1    10 

18 

8750 

1 

10 

18 

7200 

1-0     9 

19 

8850 

1-0 

9 

19 

7300 

3-0     8 

20 

8900 

2-0  |   8^ 

20 

7400 

5-0 

7 

21 

9050 

3-0  - 

8 

21 

7500 

5-0 

22 

9100 

4-0 

iy2 

22 

7600 

6-0 

6% 

23 

9150 

5-0 

7 

23 

7700 

6-0 

24 

9200 

6-0 

6% 

24 

7800 

7-0 

6 

28 

9500 

1%" 

7-0 

6 

28 

7900 

1%" 

8-0 

5% 

32 

9500 

8-0 

5%  ' 

32 

7900 

9-0 

5 

34 

9600 

9-0 

5 

34 

7900 

10-0 

4% 

36 

9700 

10-0 

4% 

36 

7900 

11-0 

4 

38 

9800 

11-0 

4 

38 

7900 

12-0 

3% 

40 

9700 

1%" 

12-0 

3% 

40 

7900 

1W 

13-0     3y2 

45 

9700 

iy2" 

13-0 

3% 

45 

7900 

14-0     3% 

50 

9700 

14-0 

3% 

50 

7900 

15-0     3 

55 

9600 

14-0 

55 

7900 

15-0 

60 

9600 

15-0 

3 

60  • 

7900 

16-0     2% 

65 

9600 

15-0 

65  ' 

7800 

16-0 

70 

9500 

16-0 

2% 

70 

7800 

17-0 

2% 

75 

9500 

16-0 

75 

7800 

17-0  • 

80 

9300 

17-0 

2% 

80  ||  7700 

18-0  1   2% 

85 

9100 

17-0 

85    7600 

18-0 

90 

9100 

1%" 

18-0 

2% 

90  '1  7400 

19-0 

2 

95 

9000 

19-0 

2 

95 

7400 

20-0 

1% 

100 

8700 

20-0 

1% 

100 

7200 

21-0 

1% 

110 

8500 

21-0 

iy2 

110 

6900  | 

22-0 

1% 

Sizes  of  Travelers  will  vary  from  the  above  table  according  to  varia- 
tions in  speed,  quality  of  cotton,  etc.,  but  the  table  may  serve  as  a  basis  to  se- 
lect from.  The  higher  the  speed  the  lighter  the  traveler  and  vice  versa, 
varying  in  proportion  of  one  or  two  grades  of  travelers  to  each  1,000  revolu- 
tions of  spindle.  Without  separators  a  few  grades  heavier  traveler  would  be 
required. 


142  COTTON    MILL    MACHINERY    CALCULATIONS 

CHAPTER  IX. 

TWISTING — COUNTS  OF  PLY  YARNS — AMOUNT  OF  TWIST — TWIST 
CALCULATIONS  AND  CONSTANT — PRODUCTION  CALCULATIONS 
AND  CONSTANT. 

Twisting  is  the  process  of  combining  two  or  more  single 
threads  into  one  by  the  simple  act  of  twisting  them  together.  The 
machine  doing  this  is  called  a  twister,  being  similar  in  general 
construction  to  the  spinning  frame.  It  does  no  drawing,  the  rolls 
being  arranged  to  grip  the  yarn  and  feed  it  forward  at  a  con- 
stant speed  to  the  spindles,  which  put  the  twist  in  the  yarn.  The 
machines  are  built  smaller  and  are  run  at  a  higher  speed  as  the 
counts  of  the  yarn  twisted  increase.  They  are  also  built  to  do 
wet  or  dry  twisting,  wet  twisting,  that  is,  passing  the  yarn 
through  water  just  before  it  reaches  the  rolls,  being  used  to  give 
the  yarn  a  smoother  finish  and  less  tendency  to  kink  from  the 
twist  present.  The  use  of  either  warp  or  filling  wind  is  possible. 

The  yarn,  after  being  twisted,  is  spoken  of  as  "ply"  yarn, 
the  word  "ply"  signifying  that  there  is  more  than  one  individual 
etrand  in  the  yarn.  As  the  ply  yarn  may  contain  two,  three  or 
more  strands  in  its  make-up,  it  is  usual  to  designate  the  number 
of  such  strands  present,  as  two-ply  or  three-ply  yarn.  The  most 
common  is  the  two-ply  or  doubled  yarn. 

The  counts  of  ply  yarns  are  given  as  the  counts  of  the  single 
yarn  of  which  it  is  composed,  with  a  figure  in  front  indicating 
the  number  of  threads  twisted  together.  If  two  single  yarns  of 
40's  counts  are  twisted  together  the  resulting  ply  yarn  would  be 
called  two  forty's  and  expressed  thus :  2/40's ;  the  figure  2  indicat- 
ing the  number  of  strands  in  the  completed  yarn  and  40  the  size 
of  the  individual  yarns.  In  calculations  for  the  weight  of  goods, 
twist  and  production,  we  must  consider  the  yarn  as  being  20's,  as 
2  strands  of  40's  yarn  is  the  equivalent  in  weight  of  a  single  20's. 
In  the  same  way  3/30's  means  a  3-ply  yarn  composed  of  3  strands 
of  30's  yarn  and  is  the  equivalent  of  a  single  10's  yarn. 

There  is  no  set  or  fixed  rule  for  determining  the  amount  of 
twist  to  put  in  twisted  yarn,  the  exact  amount  depending  upon  the 
purpose  for  which  the  product  is  to  be  used  and,  as  this  varies  to 
a  very  great  extent,  the  twist  will  vary  also.  In  making  two-ply 
yarns  for  market,  it  is  usual  to  twist  the  single  yarns  slacker  than 
warp  twist  and  use  four  as  a  multiplier  for  twist  in  the  ply  yarn. 
In  filling  orders  it  is  usual  for  the  buyer  to  state  the  amount  of 
twist  desired  and  the  mill  puts  that  amount  in  the  yarn.  Yarns 
for  weaving  are  spun  and  twisted  slacker  than  warp ;  if  for  mer- 


TWISTERS. 


143 


cerizing  the  amount  of  twist  is  less  than  filling.  The  hardest 
twisted  yarns  are  those  intended  for  lace  work  and  sewing  thread, 
while  the  softest  twisted  yarns  are  those  intended  for  crochet  and 
embroidery  yarns. 

The  general  rule  is  to  spin  the  yarn  with  regular  or  "warp" 
twist  and  twist  with  reverse  twist,  that  is  the  spindles  of  the 
twister  will  revolve  in  an  opposite  direction  to  those  on  the  spin- 


FIG.  44.    DIAGRAM  OF  GEARING  ON  THE  FALES  &  JENKS  TWISTER. 


ning  frame.  This  is  always  done  in  making  two-ply  yarns,  but 
is  not  necessarily  held  to  in  making  yarns  for  special  purposes, 
where  the  yarn  is  doubled  and  twisted  and  the  ply  yarns  again 
twisted  making  a  4-ply  yarn  or  higher. 

In  calculating  the  amount  of  twist  for  ply  yarns,  the  fig- 
ures are  always  based  on  its  equivalent  to  single  yarn.  For  illus- 
tration, the  twist  put  in  2/50's,  using  4  as  a  twist  multiplier, 
would  be  as  follows : 

2/50's  is  the  equivalent  of  a  single  25's,  then :  V  25  X  4  =  20 
turns  per  inch  twist  in  the  yarn. 


144  COTTON    MILL    MACHINERY    CALCULATIONS 

In  the  same  way  3/50's  would  have :  V  16.67  x  4  =  16.33 
turns  of  twist  per  inch. 

Fig.  44  shows  a  cut  of  the  geared  end  of  a  twister  built  by 
Fales  &  Jenks  Machine  Co.,  Pawtucket,  R.  I.  This  type  of  gearing 
is  similar  to  most  twisters  and  consists  of  two  front  roll  gears  of 
112  teeth,  driven  by  two  large  intermediates  that  are  in  gear 
with  each  other.  One  of  the  intermediates  is  driven  by  the  twist 
change  gear  which  is  carried  on  the  stud  with  the  jack  gear  of 
96  teeth.  The  cylinder  or  drum  gear  of  30  teeth,  located  on  the 
end  of  the  cylinder,  drives  the  jack  gear.  The  roll  is  l1/^  inches 
in  diameter,  the  cylinder  8  inches  in  diameter  and  the  whorl  on 
the  spindle  is  1  inch  in  diameter.  The  ratio  of  the  cylinder  to 
the  whorl  is  1  to  7.04. 

The  twist  constant  is  found  by  the  same  method  as  used  on 
the  spinning  frame.  The  circumference  of  the  IVs  inch  roll  is 
4.71  inches. 

112X  96X7.04 

—  =  twist  constant. 
4.71XXX30 

Constant  -r-  Gear  =  Twist  per  inch. 
Constant  -r-  Twist  per  inch  =  Gear. 

There  is  a  large  range  of  twist  possible  with  this  frame,  and 
its  construction  allows  the  cylinder  gear  to  be  varied  considerably 
without  changing  the  size  of  the  jack  gear,  the  cylinder  and  twist 
gears  being  interchangeable,  thus  giving  two  or  more  sets  of 
twists  for  the  same  set  of  change  gears.  In  another  model  of  this 
rrachine,  using  compound  twist  gearing,  the  gears  being  inter- 
changeable, it  is  possible  to  get  almost  any  desired  range  of  twist 
with  but  few  gears  carried  in  stock. 

Fig.  45  shows  a  cut  of  the  geared  end  of  the  Hopedale  twister, 
built  by  the  Draper  Co.,  Hopedale,  Mass.  This  gearing  is  sim- 
iJar  to  the  one  just  shown.  In  this  case,  however,  the  gear  on 
the  end  of  the  drum  is  the  change  gear.  The  drum  or  twist 
change  gear  and  the  stud  gear  are  interchangeable,  the  pin  carry- 
ing the  jack  and  stud  gears,  working  in  a  slot  in  the  jack  gear 
arm,  is  movable  thus  allowing  a  change  in  the  distance  between 
gear  centers  which  permits  >  the  using  of  any  size  drum  gear 
without  any  change  in  the  size  of  the  jack  gear.  With  this 
arrangement  and  a  few  extra  gears  it  is  possible  to  get  almost 
any  desired  twist. 

,     With  the  roll  li/2  inch,  drum  8  inches  and  whorl  1  inch  in 
diameter,  the  following  gives  the  twist  constant: 

90X120X7.04 

—  =  504  twist  constant. 
4.71X32XX 


TWISTERS.  145 

Constant  -f-  Gear  =  Twist. 

Constant  -r-  Twist  =  Gear. 

Then  a  twist  gear  of  30  teeth  will  give  16.8  turns  per  inch 
twist,  as  follows :  504  -f-  30  =  16.8. 

If  the  stud  gear  is  changed  we  get  an  entirely  new  value 
to  the  train  of  gearing  and  consequently  a  different  set  of  twists 
for  the  same  twist  gears.  Suppose  we  put  on  a  36  tooth  gear  in 
place  of  the  32  tooth  stud  gear.  This  will  have  the  effect  of  in- 
creasing the  front  roll  speed  thus  decreasing  the  twist.  We  can 
then  get  our  new  constant  as  follows : 

Mutiply  the  present  constant  by  the  stud  gear  on  the  frame 
and  divide  by  the  stud  gear  that  is  to  be  used.  32  X  504  -4-  36  = 
448  twist  constant  with  36  tooth  stud  gear. 

A  twist  gear  of  30  teeth  will  give  only  14.9  turns  of  twist 
instead  of  16.8  as  before,  as:  448  -^-30—  14.9  turns  of  twist. 

This  variation  from  the  former  standard  will  be  present  in 
the  same  proportion  with  all  the  twist  gears  used,  so  it  will  be 
seen  how  easy  it  is  to  obtain  a  new  set  of  twists  with  the  use  of 
1he  same  gears. 

PRODUCTION. 

The  production  of  a  twister  depends  upon  the  spindle  speed, 
the  twist  in  the  yarn,  the  size  of  the  yarn  and  the  time  lost.  It 
can  be  figured  from  the  size  of  the  yarn  and  the  roll  delivery,  or 
from  the  spindle  speed,  size  of  yarn  and  the  twist.  The 
time  lost  while  doffing,  creeling  and  oiling  varies  with  the  size 
of  the  yarn,  the  amount  of  twist  run,  the  number  of  the  ply  and 
the  size  of  the  bobbins  made,  being  greatest  when  running  the 
lower  numbers  of  yarn. 

Example:  A  twister  on  2/30's  yarn  has  a  front  roll  speed 
of  80  R.  P.  M.  Time  lost  10  per  cent.  Diameter  of  front  roll 
li/fc  inch.  What  is  the  production  per  spindle  for  a  10  hour  day? 
Circumference  of  the  1^  inch  roll  is  4.71  inches. 

4.71X80X10X60X.9 

—  =  .448    pounds. 
36X15X840 

In  the  above  calculation  15  is  used  instead  of  30  as  the  yarn 
after  twisting  is  the  equivalent  of  a  single  15's  yarn. 

If  we  consider  10  per  cent  to  be  a  good  fair  average  for  loss 

'of  time  while  doffing,  oiling,  etc.,  we  can  see  that  there  are  only 

two  variable  quantities  in  the  above  production  calculation,  the 

speed  of  the  roll  and  the  size  of  the  yarn.    Now  if  we  leave  these 


146 


COTTON    MILL    MACHINERY    CALCULATIONS 


two  quantities  out  and   work   out   the   value   of   the    remaining 
figures  we  get  the  production  constant,  as  follows : 

4.71  X 10  X  60  X. 9 

—  =  .0841  production  constant. 
36X840 

If  the  production  constant  is  multiplied  by  the  roll  «.peed  ?nd 


FIG.  45.    TWIST  GEARING.  ON  THE  DRAPER  TWISTER. 

divided  by  the  equivalent  counts  of  the  twisted  yarn,  the  result 
will  be  the  production  per  spindle,  as  follows : 

.0841X80  -4- 15  =  .448  pounds  per  spindle. 

It  will  be  noticed  that  this  gives  the  same  result  as  obtained 
in  the  first  calculation.  This  constant  only  holds  good  on  frames 
with  a  iy$  inch  roll  and  is  based  on  a  10  hour  day  With  a  10  per 
cent  allowance  for  loss  of  time. 

When  two  yarns  are  twisted  together  there  is  a  tendency  for 
the  yarns  to  contract  and  become  shorter.  This  increases  the 
weight  of  the  yarn,  causing  it  to  be  heavier  than  is  expected.  The 
amount  of  this  contraction  varies  with  the  amount  of  twist  put  in 
both  the  single  and  the  ply  yarns.  If  two  hard  twisted  single 


TWISTERS.  147 

yarns  were  doubled  and  twisted  slack,  the  tendency  to  contract 
and  become  heavier  might  be  overcome  by  the  opposite  action 
going  on  in  the  single  yarns.  Under  most  conditions  there  is  a 
contraction  of  the  twisted  yarns  and  to  overcome  this  heavying 
up  of  the  yarn  while  being  twisted  it  is  usual,  where  accuracy  is 
desired  in  the  size  of  the  finished  yarn,  to  spin  the  single  yarns  a 
number  or  so  lighter.  In  this  case  what  is  called  2/40's  is  not 
twisted  from  40's  yarn  but  from  41's  or  42's  single  yarn.  The 
amount  of  variation  in  the  numbers  depending  upon  the  amount 
of  contraction  in  twisting  and  this  in  turn  depending  upon  the 
amount  of  twist  in  the  yarns. 


148 


COTTON    MILL    MACHINERY    CALCULATIONS 


SIZE  OF  TRAVELLERS. 

There  can  be  given  no  rule  for  determining  the  size  travellers 
to  use  in  twisting,  as  they  vary  according  to  varying  conditions 
of  twist,  speed,  size  of  ring  and  bobbin,  length  of  traverse,  etc.  The 
only  method  of  getting  the  exact  size  to  use  is  by  experimenting 
with  the  different  numbers,  finally  selecting  the  size  that  seems 
to  give  the  best  results.  However,  below  is  given  a  table  that 
will  serve  simply  as  a  guide  and  not  intended  to  be  exact.  It  is 
for  dry  twisting  two-ply  yarns  with  4  as  a  twist  multiplier  and 
a  ring  2"  for  the  coarser  numbers  and  l%r/  in  diameter  for  the 
finer  numbers. 


TABLE  OF  TRAVELLERS. 

SIZE  OF  YARN. 

SIZE  TRAVELLER. 

10 

14's 

12 

14's 

14 

13's 

16 

12's 

18 

ll's 

20 

10's 

22 

10's 

24 

9's 

26 

8's 

28 

8's 

30 

7's 

32 

7's 

34 

6's 

36 

6's 

38 

5's 

40 

5's 

44 

4's 

46 

,.   3's 

50 

2's 

60 

1-0 

70 

3-0 

80 

6-0 

90 

9-0 

100 

11-0 

110 

14-0 

120 

16-0 

PRODUCTION    TABLE    FOR    TWISTING 


TWO  PLY  PRODUCTION  TABLE 

POUNDS    PER    SPINDLE    PER    WEEK    OF    58    HOURS 

MULTIPLIER  2 

MULTIPLIERS 

MULTIPLIER  4 

Number 

% 

y 

R.P.M. 

R.P.M. 

Pounds 

R.P.M. 

R.P.M. 

Pounds 

R.P.M. 

R.P.M. 

Pounds 

of 

of 

of 

of 

Yarn 

IJin. 
Roll 

of 
Spindle 

per 
Spindle 

IJin. 
Roll 

of 
Spindle 

per 
Spindle 

IJin. 
Roll 

of 

Spindle 

per 
Spindle 

4, 

'if 

3" 

187 

2500 

38.01 

175 

350O 

37.03 

142 

3800 

31.0O 

5 

" 

ii 

182 

2700 

30.99 

164 

370O 

29.00 

133 

400O 

24.09 

6 

tt 

ii 

178 

2900 

26.05 

155 

380O 

23.38 

125 

4100 

19.32 

7 

ii 

175 

3100 

22.36 

147 

3900 

19.28 

119 

4200 

15.95 

8 

" 

" 

172 

330» 

19.53 

141 

40OO 

16.39 

114 

4300 

13.49 

9 

31" 

2.f 

169 

3400 

17.26 

137 

4100 

14.30 

no 

4400 

11.66 

10 

a 

166 

3500 

15.4O 

133 

4200 

12.61 

107 

4500 

10.29 

11 

ii 

163 

3600 

13.87 

130 

4300 

11.28 

104 

4600 

9.16 

12 

'• 

ii 

160 

3700 

12.56 

127 

4400 

10.16 

102 

4700 

8.28 

13 

« 

158 

3800 

11.52 

125 

4500 

9.27 

100 

4800 

7.53 

14, 

ii 

156 

3900 

10.61 

123 

4,600 

8.51 

98 

4900 

6.87 

15 

" 

" 

155 

4000 

9.87 

121 

4700 

7.84 

97 

5000 

6.37 

16 

3i" 

2J' 

154 

4100 

9.22 

120 

4800 

7.31 

96 

5100 

5.93 

17 

M 

153 

4200 

8.64 

119 

4900 

6.84 

95 

5200 

5.53 

18 

" 

ii 

152 

4300 

8.13 

118 

5000 

6.42 

94 

5300 

5.18 

19 

«t 

151 

4400 

7.66 

117 

5100 

6.04 

93 

5400 

4.86 

20 

H 

150 

4500 

7.24 

116 

5200 

5.69 

92 

5500 

4.58 

22 

It 

'  ii 

147 

4600 

6.46 

113 

5300 

5.05 

90 

5600 

4.08 

24 

" 

" 

144 

4700 

5.82 

no 

5400 

4.52 

88 

5700 

3.66 

^26 

3" 

2" 

141 

4800 

5.27 

107 

5500 

4.07 

86 

580O 

3.31 

28 

ii 

139 

4900 

4.83 

105 

5600 

3.71 

84 

5900 

3.01 

30 

137 

5000 

4.46 

103 

5600 

3.41 

82 

6000 

2.74 

32 

.  tt 

135 

5100 

4.13 

101 

5700 

3.14 

80 

6000 

2.51 

34 

« 

« 

134 

5200 

3.86 

99 

5800 

2.90 

78 

6100 

2.31 

36 

n 

<t 

133 

5300 

3.62 

97 

5800 

2.68 

76 

6100 

2.13 

38 

" 

«* 

132 

5400 

3.41 

96 

5900 

2.52 

75 

6200 

1.99 

40 

2|» 

1|' 

131 

5500 

3.22 

95 

6000 

2.37 

74 

6200 

1.87 

42 

M 

>i 

130 

5600 

3.05 

94 

6100 

2.24 

73 

6300 

1.76 

44 

>l 

<• 

129 

5700 

2.89 

93 

6200 

2.11 

72 

6400 

1.66 

46 

II 

ii 

128 

5800 

2.75 

92 

6200 

2.00 

71 

6400 

1.56 

5O 

n 

« 

126 

5900 

2.49 

90 

6300 

1.80 

69 

6500 

1.40 

55 

it 

123 

6100 

2.21 

87 

6400 

1.59 

66 

6500 

1.22 

60 

" 

12O 

6200 

1.98 

84 

6500 

1.41 

64 

6600 

1.08 

65 

2f" 

11* 

117 

6300 

1.78 

82 

6600 

1.27 

62 

6700 

.97 

7O 

it 

115 

6400 

1.63 

80 

6700 

1.16 

6O 

6700 

.87 

75 

.. 

113 

6500 

1.50 

78 

6700 

1.05 

58 

6700 

.79 

80 

ii 

111 

6600 

1.38 

76 

6800 

.96 

57 

6300 

.73 

85 

ii 

74 

6800 

.88 

5(5 

6900 

.67 

90 

ii 

•  < 

72 

6800 

.81 

55 

7000 

.62 

95 

" 

70 

6800 

.75 

54 

7000 

.58 

100 

2i" 

U" 

69 

6900 

.70 

53 

7100 

.54 

110 

ii 

66 

6900 

.61 

51 

7100 

.4,7 

12O 

tt  ' 

II 

63 

6900 

.53 

49 

7100 

.42 

13O 

ii 

" 

47 

7100 

.37 

14,0 

a 

« 

45 

7100 

.33 

150 

" 

II 

44 

7200 

.30 

160 

" 

" 

43 

7200 

.28 

PRODUCTION    TABLE    FOR    TWISTING 


TWO  PLY  PRODUCTION  TABLE 

(Continued) 

POUNDS    PER    SPINDLE    PER    WEEK    OF   58    HOURS 

MULTIPLIER  5 

MULTIPLIER  6 

MULTIPLIER  7 

Number 

1 

? 

R.P.M 

R.P.M. 

Pounds 

R-p;"-|  R.P.M. 

Pounds 

R.P.M 

R.P.M. 

Pounds 

of 

of 

of    1 

of 

Y.rn 

u 

Of 

IJin. 
Roll 

of 
Spindle 

per 
Spindle 

4  in. 
Roll 

Spindle 

per 
Spindle 

11  in. 

Roll 

of 

Spindle 

per 

Spindle 

4, 

4," 

3" 

12O 

4000 

26.84 

102 

4100 

23.23 

90 

4200 

20.87 

5 

« 

M 

111 

4100 

20.59 

94 

42OO 

17.64 

82 

4300 

15.62 

6 

" 

« 

104 

4200 

16.37 

88 

4300 

14.05 

77 

440O 

12.46 

7 

II 

98 

4300 

13.38 

83 

440O 

11.46 

73 

4500 

10.20 

8 

" 

" 

93 

440O 

11.21 

80 

450O 

9.73 

70 

46OO 

8.61 

9 

ay 

ay 

9O 

4500 

9.71 

77 

46OO 

8.38 

67 

4700 

7.36 

10 

87 

4600 

8.49 

74 

4700 

7.27 

65 

4800 

6.44 

11 

a 

ii 

85 

470O 

7.58 

72 

4800 

6.46 

63 

4900 

5.70 

12 

« 

83 

48OO 

6.80 

70 

490O 

5.78 

62 

5000 

5.15 

13 

" 

81 

4900 

6.15 

69 

5000 

5.27 

61 

5100 

4.69 

14, 

" 

80 

5000 

5.66 

68 

51OO 

4.84 

6O 

5200 

4.29 

15 

•< 

" 

79 

5100 

5.23 

67 

5200 

4.46 

59 

5300 

3.95 

16 

3i" 

~  -L 

78 

520O 

4.85 

66 

5300 

4.13 

58 

5400 

3.64 

IT 

77 

5300 

4.52 

65 

5400 

3.83 

57 

5500 

3.38 

18 

" 

" 

76 

5400 

4.22 

64 

5400 

3.57 

56 

5500 

3.13 

19 

II 

75 

5400 

3.95 

63 

5500 

3.33 

55 

5600 

2.92 

20 

ii 

.1 

74 

5500 

3.70 

62 

5500 

3.12 

55 

5700 

2.77 

22 

" 

" 

72 

5600 

3.28 

61 

570O 

2.79 

54 

5900 

2.48 

24, 

" 

70 

5700 

2.93 

6O 

5900 

2.52 

53 

6100 

2.23 

26 

3" 

2* 

68 

5800 

2.63 

59 

6000 

2.29 

52 

62OO 

2.02 

28 

" 

.» 

67 

5900 

2.41 

58 

6100 

2.09 

51 

6300 

1.85 

SO 

<« 

66 

6000 

2.22 

57 

6200 

1.92 

50 

6400 

1.69 

32 

« 

65 

610O 

2.05 

56 

63OO 

1.77 

49 

6500 

1.55 

34. 

«< 

64, 

6200 

1.90 

55 

6400 

.64 

48 

6500 

1.43 

36 

ii 

M 

63 

630O 

1.77 

54 

6500 

.52 

47 

6600 

1.33 

38 

" 

62 

6400 

1.65 

53 

6500 

.42 

46 

6600 

1.23 

4O 

2V 

ir 

61 

6400 

1.55 

52 

6600 

1.32 

45 

6600 

1.15 

4,2 

60 

6500 

1.45 

51 

6600 

1.24 

44 

6700 

1.07 

44. 

ii 

ii 

59 

6500 

1.36 

5O 

66OO 

.16 

43 

670O 

.1.00 

46 

ii 

•• 

58 

6600 

1.28 

49 

6600 

1.O9 

42 

6700 

.93 

60 

.. 

56 

6600 

1.14 

47 

6600 

.96 

41 

6800 

.84 

55 

" 

.. 

54, 

6700 

.98 

46 

6800 

.85 

4O 

6900 

.74 

6O 

" 

52 

6700 

.88 

45 

7000 

.77 

39 

7000 

.67 

65 

-  *'  ' 

ir 

50 

6700 

.79 

44 

71OO 

.69 

38 

7100 

.60 

70 

•' 

49 

68OO 

.72 

43 

7200 

.63 

37 

720O 

.54 

75 

" 

i< 

48 

6900 

.65 

42 

730O 

.57 

36 

7300 

.49 

80 

ii 

47 

7000 

.60 

41 

7300 

.53 

35 

7*00 

.45 

85 

ii 

46 

710O 

.55 

40 

7400 

.48 

35 

750O 

.42 

90 

ii 

45 

7100 

.51 

39 

7400 

.45 

34 

75OO 

.39 

95 

" 

44 

7100 

.47 

38 

7400 

.41 

33 

7500 

.36 

100 

sy 

il" 

43 

7200 

.44 

37 

7400 

.38 

32 

7500 

.33 

110 

" 

•' 

41 

7200 

.38 

35 

7400 

.33 

30 

7500 

.28 

120 

" 

" 

39 

7200 

.33 

34 

7400 

29 

29 

7500 

.25 

130 

«' 

M 

38 

7200 

.30 

14.0 

II 

37 

730O 

.27 

150 

II 

36 

7300 

.25 

160 

" 

" 

35 

7400 

.22 

TWIST    TABLE    FOR    TWISTING 


TWO 

PLY  TWIST  TABLE 

No.  of 

No.  of 

Sq.  Root 

TWIST    PER    INCH 

Yarn 
to  be 

Twisted 

of  No.  of 
Twisted 

Square  Root  Multiplied  by 

Twisted 

Yarn 

Yarn 

1* 

2 

2* 

3 

3* 

4 

4* 

1 

.5 

.707 

1.06 

1.41 

1.77 

2.12 

2.47 

2.83 

3.18 

2 

1.0 

1.000 

1.50 

2.00 

2.50 

3.00 

3.50 

4.0O 

4.50 

3 

1.5 

1.225 

1.84 

2.45 

3.06 

3.68 

4.29 

4.90 

5.51 

4* 

2.0 

1.414 

2.12 

2.83 

3.54 

4.24 

4.95 

5.66 

6.36 

5 

2.5 

1.581 

2.37 

3.16 

3.95 

4.74 

5.53 

6.32 

7.11 

'6 

3.0 

1.732 

2.60 

3.46 

4.33 

5.20 

6.06 

6.93 

7.79 

7 

3.5 

1.871 

2.81 

3.74 

4.68 

5.61 

6.55 

7.48 

8.42 

8 

4.O 

2.000 

3.00 

4.00 

5.00 

6.00 

7.00 

8.00 

9.00 

9 

4.5 

2.121 

3.18 

4.24 

5.30 

6.36 

7.42 

8.48 

9.54 

1O 

5.0 

2.236 

3.35 

4.47 

5.59 

6.71 

7.83 

8.94 

10.06 

11 

5.5 

2.345 

3.52 

4.69 

5.86 

7.04 

8.21 

9.38 

10.55 

12 

6.O 

2.450 

3.68 

4.90 

6.13 

7.35 

8.58 

9.80 

11.03 

13 

6.5 

2.550 

3.83 

5.10 

6.38 

7.65 

8.93 

10.20 

11.48 

14 

7.0 

2.646 

3.97 

5.29 

6.62 

7.94 

9.26 

10.58 

11.91 

15 

7.5 

2.739 

4.11 

5.48 

6.85 

8.22 

9.59 

10.95 

12.33 

16 

8.0 

2.828 

4.24 

5.66 

7.07 

8.48 

9.90 

11.31 

12.73 

17 

8.5 

2.916 

4.37 

5.83 

7.29 

8.75 

10.21 

11.66 

13.12 

18 

9.O 

3.000 

4.50 

6.00 

7.50 

9.OO 

1O.5O 

12.OO 

13.50 

19 

9.5 

3.082 

4.62 

6.16 

7.71 

9.25 

1O.79 

12.33 

13.87 

20 

10.0 

3.162 

4.74 

6.32 

7.91 

9.49 

11.07 

12.65 

14.23 

21 

10.5 

3.240 

4.86 

6.48 

8.10 

9.72 

11.34 

12.96 

14.58 

22 

11.0 

3.317 

4.98 

6.63 

8.29 

9.95 

11.61 

13.27 

14.93 

23 

11.5 

3.391 

5.09 

6.78 

8.48 

10.17 

11.87 

13.56 

15.26 

24. 

12.0 

3.464 

5.20 

6.93 

8.66 

10.39 

12.12 

13.86 

15.59 

25 

12.5 

3.536 

5.30 

7.07 

8.84 

10.61 

12.38 

14.14 

15.91 

26 

13.0 

3.606 

5.41 

7.21 

9.02 

10.82 

12.62 

14.42 

16.23 

27 

13.5 

3.674 

5.51 

7.35 

9.19 

11.02 

12.86 

14.70 

16.53 

28 

14.  0 

3.742 

5.61 

7.48 

9.36 

11.23 

13.10 

14.97 

16.84 

29 

14.5 

3.808 

5.71 

7.62 

9.52 

11.42 

13.33 

15.23 

17.14 

30 

15.0 

3.873 

5.81 

7.75 

9.68 

11.62 

13.56 

15.49 

17.43 

31 

15.5 

3.937 

5.91 

7.87 

9.84 

11.81 

13.78 

15.75 

17.72 

32 

16.0 

4.OOO 

6.00 

8.00 

10.00 

12.00 

14.00 

16.  OO 

18.00 

33 

16.5 

4.062 

6.09 

8.12 

10.16 

12.19 

14.22 

16.25 

18.28 

34. 

17.0 

4.123 

6.18 

8.25 

10.31 

12.37 

14.43 

16.49 

18.55 

35 

17.5 

4.183 

6.27 

8.37 

10.46 

12.55 

14.64 

16.73 

18.82 

36 

18.0 

4.243 

6.36 

8.49 

10.61 

12.73 

14.85 

16.97 

19.09 

37 

18.5 

4.301 

6.45 

8.60 

10.75 

12.90 

15.05 

17.20 

19.35 

38 

19.0 

4.359 

6.54 

8.72 

10.  9O 

13.08 

15.26 

17.44 

19.62 

39 

19.5 

4.416 

6.62 

8.83 

11.04 

13.25 

15.46 

17.66 

19.87 

40 

20.0 

4.472 

6.71 

8.94 

11.18 

13.42 

15.65 

17.89 

20.12 

4.1 

20.5 

4.528 

6.79 

9.06 

11.32 

13.58 

15.85 

18.11 

20.37 

4.2 

21.0 

4.583 

6.87 

9.17 

11.46 

13.75 

16.  04 

18.33 

20.62 

4.3 

21.5 

4.637 

6.96 

9.27 

11.59 

13.91 

16.23 

18.55 

20.87 

4,4, 

22.  0 

4.690 

7.04 

9.38 

11.73 

14.07 

16.42 

18.76 

21.11 

4-5 

22.5 

4.743 

7.11 

9.49 

11.86 

14.23 

16.60 

13.97 

21.34 

4,6 

23.0 

4.796 

7.19 

9.59 

11.99 

14.39 

16.79 

19.18 

21.58 

4,7 

23.5 

4.848 

7.27 

9.70 

12.12 

14.54 

16.97 

19.39 

21.82 

4,8 

24.  0 

4.899 

7.35 

9.80 

12.25 

14.70 

17.15 

1P.6O 

22.05 

4,9 

24.5 

4.950 

7.43 

9.9O 

12.38 

14.85 

17.33 

19.80 

22.28 

50 

25.0 

5.000 

7.50 

10.00 

12.  5O 

15.0O 

17.50 

20.00 

22.50 

51 

25.5 

5.050 

7.58 

10.10 

12.63 

15.15 

17.68 

20.20 

22.73 

52 

26.  0 

5.099 

7.65 

10.20 

12.75 

15.30 

17.85 

20.  4O 

22.95 

53 

26.5 

5.148 

7.72 

10.  3O 

12.87 

15.44 

18.02 

20.59 

23.17 

54. 

27.0 

5.196 

7.79 

1O.39 

12.99 

15.59 

18.19 

20.78 

23.38 

55 

27.5 

5.244 

7.87 

10.49 

13.11 

15.73 

18.35 

20.98 

23.60 

56 

28.0 

5.292 

7.94 

10.58 

13.23 

15.88 

18.52 

21.17 

23.81 

57 

28.5 

5.339 

8.O1 

10.68 

13.35 

16.02 

18.69 

21.36 

24.03 

58 

29.0 

5.385 

8.08 

10.77 

13.46 

16.16 

18.85 

21.54 

24.23 

59 

29.5 

5.431 

8.15 

10.86 

13.58 

16.29 

19.01 

21.73 

24.44 

60 

30.0 

5.477 

8.22 

10.95 

13.69 

16.43 

19.17 

21.91 

24.65 

TWIST  TABLE  FOR  TWISTING 


TWO  PLY  TWIST  TABLE-ccon^ 

No.  of 

No.  of 

Sq.  Root 

TWIST   PER   INCH 

Yarn 
to  be 

Twisted 

of  No.  of 
Twisted 

Square  Root  Multiplied  by 

Twisted 

Yarn 

Yarn 

5 

5* 

6 

61 

7 

71 

8 

1 

.5 

.707 

3.54 

3.89 

4.24 

4.60 

4.95 

5.30 

5.66 

2 

1.0 

l.OOO 

5.00 

5.50 

6.OO 

6.50 

7.OO 

7.50 

8.00 

3 

1.5 

1.225 

6.13 

6.74 

7.35 

7.96 

8.58 

9.19 

9.80 

4, 

2.0 

1.414 

7.07 

7.78 

8.49 

9.19 

9.90 

10.61 

11.31 

5 

2.5 

1.581 

7.91 

8.70 

9.49 

10.28 

11.07 

11.86 

12.65 

6 

3.0 

1.732 

8.66 

9.53 

10.39 

11.26 

12.12 

12.99 

13.86 

7 

3.5 

1.871 

9.36 

10.29 

11.22 

12.16 

13.10 

14.03 

14.97 

8 

4.0 

2.000 

10.00 

11.00 

12.00 

13.00 

14.00 

15.00 

16.00 

9 

4.5 

2.121 

10.61 

11.67 

12.73 

13.79 

14.85 

15.91 

16.97 

1O 

5.0 

2.236 

11.18 

12.30 

13.42 

14.53 

15.65 

16.77 

17.89 

11 

5.5 

2.345 

11.73 

12.90 

14.07 

15.24 

16.42 

17.59 

18.76 

1.2 

6.0 

2.450 

12.25 

13.48 

14.70 

15.93 

17.15 

18.38 

19.60 

13 

6.5 

2.550 

12.75 

14.03 

15.  3O 

16.58 

17.85 

19.13 

20.40 

14. 

7.0 

2.646 

13.23 

14.55 

15.87 

17.20 

18.52 

19.85 

21.17 

15 

7.5 

2.739 

13.69 

15.06 

16.43 

17.80 

19.17 

20.54 

21.91 

16 

8.O 

2.828 

14.14 

15.55 

16.97 

18.38 

19.80 

21.21 

22.62 

17 

8.5 

2.916 

14.58 

16.04 

17.49 

18.95 

20.41 

21.87 

23.33 

18 

9.0 

3.000 

15.00 

16.50 

18.00 

19.50 

21.00 

22.50 

24.00 

19 

9.5 

3.082 

15.41 

16.95 

18.49 

20.03 

21.57 

23.12 

24.66 

20 

10.0 

3.162 

15.81 

17.39 

18.97 

20.55 

22.13 

23.72 

25.30 

21 

10.5 

3.240 

16.20 

17.82 

19.44 

21.06 

22.68 

24.30 

25.92 

22 

11.0 

3.317 

16.58 

18.24 

19.90 

21.56 

23.22 

24.88 

26.54 

23 

11.5 

3.391 

16.96 

18.65 

20.35 

22.  04 

23.74 

25.43 

27.13 

24. 

12.0 

3.464 

17.32 

19.05 

20.78 

22.52 

24.25 

25.98 

27.71 

25 

12.5 

3.536 

17.68 

19.45 

21.21 

22.98 

24.75 

26.52 

28.29 

26 

13.0 

3.606 

18.03 

19.83 

21.63 

23.44 

25.24 

27.05 

28.85 

27 

13.5 

3.674 

18.37 

20.21 

22.05 

23.88 

25.72 

27.56 

29.39 

28 

14.0 

3.742 

18.71 

20.58 

22.45 

24.32 

26.19 

28.07 

29.94 

29 

14.5 

3.808 

19.04 

20.94 

22.85 

24.75 

26.66 

28.56 

30.46 

30 

15.0 

3.873 

19.37 

21.30 

23.24 

25.17 

27.11 

29.05 

30.98 

31 

15.5 

3.937 

19.69 

21.65 

23.62 

25.59 

27.56 

29.53 

31.50 

32 

16.O 

4.00O 

20.00 

22.00 

24.00 

26.00 

28.00 

30.00 

32.00 

33 

16.5 

4.062 

20.  31 

22.34 

24.37 

26.40 

28.43 

30.47 

32.50 

34, 

17.0 

4.123 

20.62 

22.68 

24.74 

26.80 

28.86 

30.92 

32.98 

35 

17.5 

4.183 

20.92 

23.01 

25.10 

27.19 

29.28 

31.37 

33.46 

36 

18.0 

4.243 

21.21 

23.34 

25.46 

27.58 

29.70 

31.82 

33.94 

37 

18.5 

4.301 

21.51 

23.66 

25.81 

27.96 

30.11 

32.26 

34.41 

38 

19.0 

4.359 

21.80 

23.97 

26.15 

28.33 

30.51 

32.69 

34.87 

39 

19.5 

4.416 

22.08 

24.29 

26.50 

28.70 

30.91 

33.12 

35.33 

4,0 

20.0 

4.472 

22.36 

24.60 

26.83 

29.07 

31.30 

33.54 

35.78 

4.1 

20.5 

4.528 

22.64 

24.90 

27.17 

29.43 

31.70 

33.96 

36.22 

4-2 

21.0 

4.583 

22.91 

25.21 

27.50 

29.79 

32.08 

34.37 

36.66 

4-3 

21.5 

4.637 

23.19 

25.50 

27.82 

30.14 

32.46 

34.78 

37.10 

4,4, 

22.0 

4.690 

23.45 

25.80 

28.14 

30.49 

32.83 

35.18 

37.52 

4.5 

22.5 

4.743 

23.72 

26.09 

28.46 

30.83 

33.20 

35.57 

37.94 

4-6 

23.  0 

4.796 

23.98 

26.38 

28.77 

31.17 

33.57 

35.97 

38.37 

4,7 

23.5 

4.848 

24.24 

26.66 

29.09 

31.51 

33.94 

36.36 

38.78 

4.8 

24.0 

4.899 

24.49 

26.94 

29.39 

31.84 

34  29 

36.74 

39.19 

4,9 

24.5 

4.950 

24.75 

27.23 

29.70 

32.18 

34.65 

37.13 

39.60 

5O 

25.0 

5.000 

25.00 

27.50 

30.00 

32.50 

35.00 

37.50 

40.00 

51 

25.5 

5.050 

25.25 

27.78 

30.30 

32.83 

35.35 

37.88 

40.40 

52 

26.0 

5.099 

25.50 

28.04 

30.59 

33.14 

35.69 

38.24 

40.79 

53 

26.5 

5.148 

25.74 

28.31 

30.89 

33.46 

36.04 

38.61 

41.18 

54, 

27.0 

5.196 

25.98 

28.58 

31.18 

33.77 

36.37 

38.97 

41.57 

55 

27.5 

5.244 

26.22 

28.84 

31.46 

34.09 

36.71 

39.33 

41.95 

56 

28.0 

5.292 

26.46 

29.11 

31.75 

34.40 

37.04 

39.69 

42.34 

57 

28.5 

5.339 

26.69 

29.36 

32.03 

34.70 

37.37 

40.04 

42.71 

58 

29.0 

5.385 

26.93 

29.62 

32.31 

35.00 

37.70 

40.39 

43.  08 

59 

29.5 

5.431 

27.16 

29.87 

32.59 

35.  3O 

38.02 

40.73 

43.45 

60 

30.0 

5.477 

27.39 

3O.12 

32.86 

35.60 

38.34 

41.O8 

43.82 

TWIST    TABLE    FOR    TWISTING 


TWO  PLY  TWIST  TABLE-ccon^ 

No.  of 

Sq.  Roo 

TWIST    PER    INCH 

No.  of 

Yarn 
to  be 

Twisted 

of  No.  of 
Twisted 

Square  Root  Multiplied  by 

Twisted 

Yarn 

Yarn 

4 

4* 

5 

5Jf 

6 

6* 

7 

61 

30.5 

5.523 

22.09 

24.85 

27.61 

30.38 

33.14 

35.90 

38.66 

63 

31.0 

5.568 

22.27 

25.06 

27.84 

30.62 

33.41 

36.19 

38.98 

63 

31.5 

5.613 

22.45 

25.26 

28.06 

30.87 

33.67 

36.48 

39.29 

64. 

32.0 

5.657 

22.63 

25.46 

28.28 

31.11 

33.94 

36.77 

39.60 

65 

32.5 

5.701 

22.80 

25.65 

28.50 

31.36 

34.21 

37.06 

39.91 

66 

33.0 

5.745 

22.98 

25.85 

28.72 

31.60 

34.47 

37.34 

40.22 

67 

33.5 

5.788 

23.15 

26.  05 

28.94 

31.83 

34.73 

37.62 

40.52 

68 

34.O 

5.831 

23.32 

26.24 

29.15 

32.07 

34.99 

37.90 

40.82 

69 

34.5 

5.874 

23.50 

26.43 

29.37 

32.31 

35.24 

38.18 

41.12 

70 

35.  0 

5.916 

23.66 

26.62 

29.58 

32.54 

35.50 

38.45 

41.41 

71 

35.5 

5.958 

23.83 

26.81 

29.79 

32.77 

35.75 

38.73 

41.71 

72 

36.0 

6.000 

24.00 

27.00 

30.00 

33.00 

36.00 

39.00 

42.00 

73 

36.5 

6.042 

24.17 

27.19 

30.21 

33.23 

36.25 

39.27 

42.29 

74, 

37.O 

6.083 

24.33 

27.37 

30.41 

33.46 

36.50 

39.54 

42.58 

75 

37.5 

6.124 

24.50 

27.56 

30.62 

33.68 

36.74 

39.81 

42.87 

76 

38.0 

6.164 

24.66 

27.74 

30.82 

33.90 

36.99 

40.07 

43.15 

77 

38.5 

6.205 

24.82 

27.92 

31.02 

34.13 

37.23 

40.33 

43.44 

78 

39.0 

6.245 

24.98 

28.10 

31.22 

34.35 

37.47 

40.59 

43.72 

79 

39.5 

6.285 

25.14 

28.28 

31.42 

34.57 

37.71 

40.85 

44.00 

80 

40.O 

6.325 

25.30 

28.46 

31.62 

34.79 

37.95 

41.11 

44.28 

81 

40.5 

6.364 

25.46 

28.64 

31.82 

35.00 

38.18 

41.37 

44.55 

82 

41.0 

6.403 

25.61 

28.81 

32.02 

35.22 

38.42 

41.62 

44.82 

S3 

41.5 

6.442 

25.77 

28.99 

32.21 

35.43 

38.65 

41.87 

45.09 

84 

42.O 

6.481 

25.92 

29.16 

32.41 

35.65 

38.88 

42.13 

45.37 

85 

42.5 

6.519 

26.08 

29.34 

32.60 

35.85 

39.11 

42.37 

45.63 

86 

43.0 

6.557 

26.23 

29.51 

32.79 

36.06 

39.34 

42.62 

45.90 

87 

43.5 

6.596 

26.38 

29.68 

32.98 

36.28 

39.57 

42.87 

46.17 

88 

44.0 

6.633 

26.53 

29.85 

33.17 

36.48 

39.80 

43.11 

46.43 

89 

44.5 

6.671 

26.68 

30.02 

33.35 

36.69 

40.02 

43.36 

46.70 

90 

45.0 

6.708 

26.83 

30.19 

33.54 

36.89 

40.25 

43.60 

46.96 

91 

45.5 

6.745 

26.98 

30.35 

33.73 

37.10 

40.47 

43.84 

47.22 

92 

46.0 

6.782 

27.13 

30.52 

33.91 

37.30 

40.69 

44.08 

47.47 

93 

46.5 

6.819 

27.28 

30.69 

34.1O 

37.50 

40.91 

44.32 

47.73 

94 

47.  0 

6.856 

27.42 

30.85 

34.28 

37.71 

41.13 

44.56 

47.99 

95 

47.5 

6.892 

27.57 

31.01 

34.46 

37.91 

41.35 

44.80 

48.24 

96 

48.0 

6.928 

27.71 

31.18 

34.64 

38.10 

41.57 

45.03 

48.50 

97 

48.5 

6.964 

27.86 

31.34 

34.82 

38.30 

41.79 

45.27 

48.75 

98 

49.0 

7.000 

28.00 

31.50 

35.00 

38.  5O 

42.00 

45.50 

49.00 

99 

49.5 

7.036 

28.14 

31.66 

35.18 

38.70 

42.21 

45.73 

49.25 

100 

50.0 

7.071 

28.28 

31.82 

35.36 

38.89 

42.43 

45.96 

49.50 

1O1 

50.5 

7.106 

28.42 

31.98 

35.53 

39.08 

42.64 

46.19 

49.74 

1O2 

51.0 

7.141 

28.56 

32.13 

35.70 

39.28 

42.85 

46.42 

49.99 

103 

51.5 

7.176 

28.70 

32.29 

35.88 

39.47 

43.06 

46.64 

50.23 

104 

52.0 

7.211 

28.84 

32.45 

36.06 

39.66 

43.27 

46.87 

50.48 

1O5 

52.5  ' 

7.246 

28.98 

32.61 

36.23 

39.85 

43.47 

47.10 

50.72 

106 

53.0 

7.280 

29.12 

32.76 

36.40 

40.04 

43.68 

47.32 

50.96 

107 

53.5 

7.314 

29.26 

32.91 

36.57 

40.23 

43.89 

47.54 

51.20 

108 

54.O 

7.349 

29.4O 

33.07 

36.74 

40.42 

44.09 

47.77 

51.44 

1O9 

54.5 

7.382 

29.53 

33.22 

36.91 

40.60 

44.29 

47.98 

51.67 

110 

55.0 

7.416 

29.66 

33.37 

37.08 

40.79 

44.50 

48.20 

51.91 

111 

55.5 

7.450 

29.80 

33.53 

37.25 

40.98 

44.70 

48.43 

52.15 

112 

56.  0 

7.483 

29.93 

33.67 

37.42 

41.16 

44.90 

48.64 

52.38 

113 

56.5 

7.517 

3O.07 

33.83 

37.58 

41.34 

45.10 

48.86 

52.62 

114 

57.0 

7.550 

30.20 

33.98 

37.75 

41.53 

45.30 

49.08 

52.85 

115 

57.5 

7.583 

30.33 

34.12 

37.91 

41.71 

45.50 

49.29 

53.08 

116 

58.0 

7.616 

30.46 

34.27 

38.08 

41.89 

45.69 

49.50 

53.31 

117 

58.5 

7.649 

3O.60 

34.42 

38.24 

42.07 

45.89 

49.72 

53.54 

118 

59.0 

7.681 

30.72 

34.56 

38.41 

42.25 

46.09 

49.93 

53.77 

119 

59.5 

7.714 

30.86 

34.71 

38.57 

42.43 

46.28 

50.14 

54.00 

120 

6O.O 

7.746 

30.98 

34.86 

38.73 

42.60 

46.48 

50.35 

54.22 

TWIST  TABLE   FOR   TWISTING 


TWO  PLY  TWIST   TABLE-^™*/ 

No.  of 

No.  of 

Sq.  Root 

TWIST   PER   INCH 

Yarn 
to  be 

Twisted 

of  No.  of 
Twisted 

Square  Root  Multiplied  by 

Twisted 

Yarn 

Yarn 

4 

41 

5 

51 

6 

61 

7 

121 

60.5 

7.778 

31.11 

35.00 

38.89 

42.78 

46.67 

50.56 

54.45 

122 

61.0 

7.810 

31.24 

35.15 

39.05 

42.96 

46.86 

50.77 

54.67 

123 

61.5 

7.842 

31.37 

35.29 

39.21 

43.13 

47.O5 

50.97 

54.89 

124 

62.0 

7.874 

31.50 

35.43 

39.37 

43.31 

47.24 

51.18 

55.12 

125 

62.5 

7.906 

31.62 

35.58 

39.53 

43.48 

47.43 

51.39 

55.34 

126 

63.0 

7.937 

31.75 

35.72 

39.69 

43.65 

47.62 

51.59 

55.56 

127 

63.5 

7.969 

31.88 

35.86 

39.84 

43.83 

47.81 

51.80 

55.78 

128 

64.0 

8.OOO 

32.00 

36.00 

40.  OO 

44.0O 

48.00 

52.00 

56.00 

129 

64.5 

8.031 

32.12 

36.14 

40.16 

44.17 

48.19 

52.20 

56.22 

130 

65.O 

8.062 

32.25 

36.28 

40.31 

44.34 

48.37 

52.4O 

56.43 

131 

65.5 

8.093 

32.37 

36.42 

40.47 

44.51 

48.56 

52.60 

56.65 

132 

66.O 

8.124 

32.50 

36.56 

40.62 

44.68 

48.74 

52.81 

56.87 

133 

66.5 

8.155 

32.62 

36.  7O 

40.77 

44.85 

48.93 

53.01 

57.09 

134 

67.0 

8.185 

32.74 

36.83 

40.93 

45.02 

49.11 

53.20 

57.30 

135 

67.5 

8.216 

32.86 

36.97 

41.08 

45.19 

49.30 

53.40 

57.51 

136 

68.0 

8.246 

32.98 

37.11 

41.23 

45.35 

49.48 

53.  6O 

57.72 

137 

68.5 

8.277 

33.11 

37.25 

41.38 

45.52 

49.66 

53.8O 

57.94 

138 

69.0 

8.307 

33.23 

37.38 

41.53 

45.69 

49.84 

54.00 

58.15 

139 

69.5 

8.337 

33.35 

37.52 

41.68 

45.85 

50.02 

54.19 

58.36 

140 

70.0 

8.367 

33.47 

37.65 

41.83 

46.02 

50.20 

54.39 

58.57 

141 

70.5 

8.396 

33.58 

37.78 

41.98 

46.18 

50.38 

54.57 

58.77 

142 

71.O 

8.426 

33.70 

37.92 

42.13 

46.34 

50.56 

54.77 

58.98 

143 

71.5 

8.456 

33.82 

38.05 

42.28 

46.51 

50.73 

54.96 

59.19 

144 

72.0 

8.485 

33.94 

38.18 

42.43 

46.67 

50.91 

55.15 

59.40 

145 

72.5 

8.515 

34.06 

38.32 

42.58 

46.83 

51.09 

55.35 

59.61 

146 

73.0 

8.544 

34.18 

38.45 

42.72 

46.99 

51.26 

55.54 

59.81 

147 

73.5 

8.573 

34.29 

38.58 

42.87 

47.15 

51.44 

55.72 

60.01 

148 

74.0 

8.602 

34.41 

38.71 

43.01 

47.31 

51.61 

55.91 

60.21 

149 

74.5 

8.631 

34.52 

38.84 

43.16 

47.47 

51.79 

56.10 

60.42 

150 

75.0 

8.660 

34.64 

38.97 

43.30 

47.63 

51.96 

56.29 

60.62 

151 

75.5 

8.689 

34.76 

39.10 

43.45 

47.79 

52.13 

56.48 

60.82 

152 

76.0 

8.718 

34.87 

39.23 

43.59 

47.95 

52.31 

56.67 

61.03 

153 

76.5 

8.746 

34.98 

39.36 

43.73 

48.10 

52.48 

56.85 

61.22 

154 

77.O 

8.775 

35.10 

39.49 

43.88 

48.26 

52.65 

57.04 

61.43 

155 

77.5 

8.803 

35.21 

39.61 

44.02 

48.42 

52.82 

57.22 

61.62 

156 

78.0 

8.832 

35.33 

39.74 

44.16 

48.58 

52.99 

57.41 

61.82 

157 

78.5 

8.860 

35.44 

39.87 

44.  3O 

48.73 

53.16 

57.59 

62.02 

158 

79.  0 

8.888 

85.58 

4O.OO 

44.44 

48.88 

53.33 

57.77 

62.22 

159 

79.5 

8.916 

35.66 

4O.12 

44.58 

49.04 

53.5O 

57.95 

62.41 

160 

80.0 

8.944 

35.78 

40.25 

44.72 

49.19 

53.66 

58.14 

62.61 

161 

80.5 

8.972 

35.89 

40.37 

44.86 

49.35 

53.83 

58.32 

62.80 

162 

81.O 

9.0OO 

36.  OO 

40.  5O 

45.00 

49.50 

54.0O 

58.50 

63.00 

163 

81.5 

9.028 

36.11 

40.63 

45.14 

49.65 

54.17 

58.68 

63.20 

164 

82.0 

9.055 

36.22 

40.75 

45.28 

49.  8O 

54.33 

58.86 

63.39. 

165 

82.5 

9.083 

36.33 

40.87 

45.42 

49.96 

54.50 

5C.04 

63.58 

166 

83.0 

9.110 

36.44 

41.  OO 

45.55 

50.11 

54.66 

59.22 

63.77 

167 

83.5 

9.138 

36.55 

41.12 

45.09 

5O.26 

54.83 

59.  4O 

63.97 

168 

84.O 

9.165 

36.66 

41.24 

45.83 

5O.41 

54.99 

59.57 

64.16 

169 

84.5 

9.192 

36.77 

41.36 

45.96 

50.56 

55.15 

59.75 

64.34 

170 

85.0 

9.220 

36.88 

41.49 

46.10 

50.71 

55.32 

59.93 

64.54 

171 

85.5 

9.247 

36.99 

41.61 

40.24 

50.86 

55.48 

60.11 

64.73 

172 

86.  0 

9.274 

37.1O 

41.73 

46.37 

51.01 

55.64 

6O.28 

64.92 

173 

86.5 

9.3O1 

37.20 

41.85 

46.51 

51.16 

55.81 

60.46 

65.11 

174 

87.0 

9.327 

37.31 

41.97 

46.64 

51.30 

55.96 

60.63 

65.29 

175 

87.5 

9.354 

37.42 

42.09 

46.77 

51.45 

56.12 

60.80 

65.48 

176 

.88.0 

9.381 

37.52 

42.21 

46.91 

51.60 

56.29 

60.98 

65.67 

177 

88.5 

9.4O7 

37.63 

42.33 

47.04 

51.74 

56.44 

61.15 

65.85 

178 

89.0 

9.434 

37.74 

42.45 

47.17 

51.89 

56.  6O 

61.32 

66.04 

179 

89.5 

9.460 

37.84 

42.57 

47.30 

52.03 

56.76 

61.49 

66.22 

180 

90.0 

9.487 

37.95 

42.69 

47.44 

52.18 

56.92 

61.67 

66.41 

ORGANIZATION  SHEETS.  155 

CHAPTER  X. 


ORGANIZATION  —  DRAFT  PRODUCTION  —  PROGRAM    OF    DRAFTS, 

WEIGHTS  AND  NUMBERS — MACHINERY  EQUIPMENT NUMBER 

OF  LOOMS. 

DRAFT  PROPORTIONING. 

To  one  who  has  had  considerable  experience  in  the  mill  in 
working  drafts,  speeds,  etc.,  on  various  sizes  of  yarn,  the  question 
of  what  size  sliver  to  run  on  drawing  to  produce  a  given  size  of 
yarn,  with  good  drafts  on  the  intervening  frames,  is  easily  settled. 
To  the  beginner  this  is  often  puzzling  and  hard  to  figure  out.  To 
either,  determining  the  exact  amount  of  draft  to  give  each 
machine,  so  as  to  have  no  unusual  drafts  at  any  point,  is  not 
always  settled  so  easily,  therefore,  the  following  rules  and  ex- 
ample will  be  useful  to  some. 

The  total  draft,  between  any  two  points  in  the  processes  of 
yarn  manufacture,  is  the  product  of  all  the  intermediate  drafts 
occurring  between  these  points. 

Taking  the  following  as  good  average  drafts  for  the  frames 
given:  Slubber,  4;  Intermediate,  5;  Fine  Frame,  6;  Spinning, 
10.5;  we  see  that  the  total  draft  on  the  above  four  machines  is 
1.260.  Now,  if  any  contemplated  lay-out  calls  for  a  total  draft 
between  these  points  inclusive,  that  is  greater  than  1,260,  the 
resulting  intermediate  drafts  will  necessarily  be  larger  than  the 
above  figures  and  the  reverse  is  also  true. 

If  it  is  proposed  to  spin  any  given  counts  of  yarn  from  any 
given  weight  of  sliver,  it  is  easy  to  determine  the  total  draft 
necessary,  by  the  following  method: 

First.  Reduce  the  grain  sliver  to  hank  sliver,  by  the  follow- 
ing rule : 

Divide  8.33  by  the  weight  of  one  yard  of  sliver,  in  grains. 

Second.     Find  the  total  draft,  by  the  following  rule: 

Multiply  the  counts  of  the  yarn  to  be  spun  by  all  the  doub- 
lings on  the  frames  and  divide  the  product  by  the  hank  sliver. 

From  the  above,  it  will  be  easy  to  determine,  for  any  given 
contemplated  lay-out,  whether  the  intermediate  drafts  will  be 
higher  or  lower  than  the  average. 

Example:  Suppose  it  is  desired  to  spin  30's  yarn  from  a  50 
grain  sliver  on  the  back  of  the  slubber,  using  three  fly  frames 
and  double  roving  on  the  spinning  frame. 

8.33  -v-  50  =  .166  hank  sliver. 


156  COTTON    MILL    MACHINERY    CALCULATIONS 

30X2X2X2 


1,445  total  draft. 


.166 

It  will  immediately  be  seen  from  this  that  the  drafts  on  the 
2'our  frames  will  be  above  the  normal  figures  given. 

The  effective  draft  is  the  amount  of  draft  that  would  be  re- 
quired to  reduce  the  sliver  to  the  desired  size  of  yarn,  if  there 
were  no  doublings,  or" it  is  the  number  of  yards  of  yarn  spun  on 
the  spinning  frame  for  each  one  yard  of  sliver  fed  into  the  back 
of  the  slubber.  If  it  is  desired  to  find  the  effective  draft,  this  can 
be  done  by  dividing  the  total  draft  by  the  product  of  the  doublings. 

Take  the  conditions  above  and  the  effective  draft  is  as 
follows : 

1445 

=  180  effective  draft. 

2X2X2 

,     Now,  the  hank  sliver  multiplied  by  the  effective  draft  will 
give  the  counts  of  the  yarn  spun : 

180  X  .166  =  29.88  or  30's  yarn. 

The  effective  draft  can  be  easiest  found  by  dividing  the 
counts  of  the  yarn  spun  by  the  hank  sliver,  as  follows: 

30  -4-  .166  =  180  effective  draft. 

You  can  figure  the  weight  of  the  sliver  to  run  to  give  any 
desired  counts  of  yarn,  using  the  above  named  average  drafts 
for  the  four  frames,  by  transposing  the  rule  for  getting  the  total 
draft.  The  rule  will  now  read  as  follows: 

Multiply  the  desired  counts  by  all  the  doublings  and  divide 
the  product  by  1,260,  which  is  the  total  draft  corresponding  to 
the  average  drafts  named.  The  result  will  be  the  hank  sliver. 
Dividing  8.33  by  the  hank  sliver  will  give  the  weight  of  the  sliver. 

The  above  results  can  be  duplicated  by  figuring  from  the 
weights  of  the  material  instead  of  using  hanks. 

Having  selected  4,  5,  6  and  10.5  as  the  average,  normal 
drafts  for  the  four  frames,  we  can  distribute,  or  divide,  the  total 
draft  of  1,445  among  the  four  frames,  considering  the  above 
figures  as  the  ratios  for  the  frames  given,  by  the  following  rule : 

Multiply  the  fourth  root  of  the  total  draft  to  be  divided  by 
(my  ratio  and  divide  the  product  by  the  fourth  root  of  the  product 
of  the  ratios.  The  result  will  be  the  draft  for  the  frame,  accord- 
ing to  which  ratio  is  used. 

This  rule  can  be  expressed  in  a  formula  which  will  show 
more  clearly  the  steps  taken : 


ORGANIZATION  SHEETS.  157 

4 

V  Total  draft  x    ratio 
=  draft  for  frame. 

^Product  of  ratios 

Note.— The  fourth  root  of  any  number  is  obtained  by  get- 
ting the  square  root  of  the  number  and  then  extracting  the 
square  root  of  this  root. 

The  product  of  the  ratios  is : 

4X5X6X10.5  =1260. 

The  fourth  root  of  1,260  =  5.95. 
The  total  draft,  as  found  above,  is  1,445. 
The  fourth  root  of  1,445  =  6.16. 

Using  the  ratio  of  10.5  for  the  spinning  frame,  we  get  the 
spinning  draft  as  follows: 

6.16X10.5 

=  10.87  spinning  draft. 

5.95 

For  the  fine  frame: 

6.16X6 


6.21  fine  frame  draft. 


5.95 

For  the  intermediate: 

6.16X5 


=  5.18  intermediate  draft. 


5.95 

For  the  slubber: 

6.16X4 


5.95 


=  4.14  slubber  draft. 


Multiplying  these  four  drafts  together  gives  a  total  draft  of 
1,447,  which  is  only  two  points  variation  from  the  1,445  started 
with. 

It  will  be  seen  from  this  that,  where  the  total  draft  is  in 
excess  of  1,260,  this  excess  will  be  proportionately  distributed 
between  the  four  intermediate  drafts  and  will  show  no  exces- 
sively high  drafts.  Herein  lies  the  advantage  in  using  this  rule 
to  map  out  the  drafts  where  there  is  no  severe  restrictions  in  the 
matter.  If  the  total  draft  were  lower  all  the  intermediate  drafts 
would  be  lower.  Another  point  gained  by  using  the  above  method 
js  that  in  no  case  will  the  result  show  an  excessive  draft  on  one 
or  more  frames  and  low  drafts  on  tne  others.  In  other  words, 


158  COTTON    MILL    MACHINERY    CALCULATIONS 

when  the  total  draft  is  high,  all  the  drafts  will  be  high  and  when 
the  total  draft  is  low,  all  the  drafts  will  be  low. 

The  numbers  4,  5,  6  and  10.5,  are  not  arbitrarily  fixed, 
where  more  or  less  draft  is  considered  advisable  on  any  of  the 
frames,  the  ratio  for  that  frame  can  be  altered  and  not  destroy 
the  efficiency  of  the  rule. 

In  running  low  numbers  of  yarn,  the  intermediate  frame 
not  being  used,  the  rule  will  apply  if  the  ratio  5  is  thrown  out  and 
the  cube  root  substituted  for  the  fourth  root.  If  using  single 
roving  in  the  spinning,  with  two  or  three  fly  frames,  change  the 
ratio  of  10.5  to  7.5  or  8  and  modify  the  formula  to  suit  the  num- 
ber of  fly  frames  used. 

ORGANIZATION  SHEET. 

In  estimating  an  organization  sheet  or  working  program  of 
drafts,  weights,  speeds,  productions  and  number  of  machines  for 
a  cotton  mill,  several  important  points  have  to  be  dealt  with. 

In  planning  for  a  new  mill  the  question  of  capacity  and  num- 
ber of  machines  is  not  very  difficult,  but,  in  planning  for  an  old 
mill,  the  most  desirable  combinations  of  drafts,  doublings  and 
speeds  have  sometimes  to  be  abandoned  and  a  less  satisfactory 
arrangement  resorted  to  in  order  to  increase  the  production  of 
some  one  class  of  machines  to  enable  them  to  keep  up  with  the 
process  ahead  and,  thus,  increase  the  total  production. 

There  is  considerable  range  to  drafts,  weights  and  speeds  on 
all  classes  of  mill  machinery  and  there  are  probably  no  two  mills 
on  the  same  class  of  goods  that  have  identically  the  same  pro- 
gram all  through  the  different  processes. 

Aside  from  the  capacity  and  proportions  of  the  machines 
available,  the  most  important  considerations  are  the  numbers  and 
qualities  of  the  yarns  made  and  the  uses  to  which  they  are  to  be 
put.  The  finest  numbers  of  yarn  and  the  better  qualities  of 
hosiery  yarns  demand  a  long  combed  stock  and  a  large  number 
of  doublings.  Coarse  yarns  for  weaving  do  not  require  such 
stock  and  the  number  of  doublings  is  decreased.  All  yarns  for 
knitting,  where  the  best  quality  is  desired,  should  be  spun  from 
combed  stock  using  the  mule,  with  double  roving  and  slack  twist, 
as  this  tends  to  greater  evenness,  smoothness  and  regularity 
and  gives  the  softest  feel  to  the  yarn. 

There  is  a  very  great  diversity  of  opinion  in  regard  to  the 
use  of  single  roving.  Many  mills  on  print  cloth,  using  28's  warp 
and  32's  filling,  spin  both  from  single  roving;  some  spin  both 
from  double  roving,  and  others  use  double  roving  on  warp,  on 
account  of  the  added  strength,  and  single  roving  on  filling.  If 
evenness  is  desired  in  coarse  yarns,  double  roving  is  often  used 


ORGANIZATION  SHEETS.  159 

and  also  in  some  cases  to  save  making  roving  of  a  different  size. 
As  fill'ng  does  not  require  so  much  strength  as  warp,  it  is  often 
spun  from  single  roving  and  the  warp*  of  about  same  size  or 
coarser,  is  spun  from  double  roving. 

In  spinning  20's  and  under  the  intermediate  roving  frame  is 
often  thrown  out  and  longer  drafts  used,  while  for  finer  yarns,  say 
60's  p^rl  Ovpr.  a  fourth  rov^ne-  frame  is  used. 

It  is  always  desirable  to  have  as  few  sizes  of  rovine-  as  pos- 
sible in  making  yarns  of  different  numbers,  and  it  often  hardens 
in  rp'lls  making  a  rane-e  of  numbers,  that  longer  and  shorter 
drafts  than  are  customary  are  used.  The  amount  of  draft  at 
the  var'ous  machines  also  depends  UDon  the  stock  being  used. 
Long  st^l«  cotton  w;H  admit  of  more  draft  than  short  staple 
cotton,  and  as  a  rule  the  draft  increases  as  the  bulk  decreases. 
In  figuring  a  program  where  there  are  no  severe  limitations, 
average  drafts  in  each  case  would  be  assumed,  varying  these 
slightly  to  brine  the  rovine-  to  standard  sizes,  remembering  that, 
within  reasonable  limits,  the  heavier  the  sliver  and  the  rovings 
and  the  longer  the  drafts,  the  smaller  the  amount  of  machinery 
necessary  to  produce  the  required  amount  of  roving. 

It  is  not  ^ossible  to  follow  a  program  of  weights  and  num- 
bers exactly,  but  where  any  degree  of  care  and  accuracy  is  taken 
in  working  it  out,  the  actual  results  obtained  will  not  vary  greatly 
from  the  figured  program. 

Thp  method  employed  to  proportion  the  different  machines 
for  a  mill  to  each  other  is  a  simple  matter.  The  production  of 
a  spinnm0"  swindle  is  usually  taken  as  the  b^sis  of  calculation  and 
all  the  other  machinery  is  laid  out  with  direct  reference  to  it. 
The  rroductions  of  the  different  machines,  under  varying  work- 
ing conditions  of  speed  and. weight  of  material  delivered,  can 
be  gotten  from  the  catalogs  issued  by  the  machine  builders  and 
will  be  found  useful  and  save  the  time  and  trouble  necessary 
to  work  them  out,  yet,  at  the  same  time,  we  ought  to  be  able  to 
do  this  work  for  ourselves  and  understand  the  methods  employ- 
ed in  getting  the  results. 

PROGRAM    OF   WEIGHTS,    DRAFTS    AND    NUMBERS. 

Assume  a  mill  of  10,000  soindles,  making  22's  yarn  for  the 
market  and  work  out  a  program  of  weights,  numbers,  drafts  and 
machinery,  or  organization  sheet. 

We  will  have  to  first  work  out  the  program  for  drafts,  weights 
and  numbers  for  the  d;fferent  processes.  The  drafts,  assuming 
that  a  50  grain  sliver  will  be  used  at  the  back  of  the  slubber, 
workf d  out  by  the  rule  given  above,  are  found  to  be  as  follows : 
Spinning,  10.05;  fine,  5.74;  intermediate,  4.79;  slubber,  3.83. 


160  COTTON    MILL    MACHINERY    CALCULATIONS 

You  will  notice  that  all  these  drafts  are  low,  which  shows  that 
a  heavier  sliver  could  easily  be  substituted  for  the  one  taken 
and  then  not  have  excessive  drafts. 

120  yards  of  22's  yarn  weigh  45.45  grains.  As  the  yarn 
contracts  and  becomes  heavier  while  being  twisted,  we  must 
allow  for  this  contraction  and  estimate  the  weight  before  it  is 
twisted  or  just  as  it  leaves  the  drawing  rolls.  This  contraction 
is  about  3%,  then: 

45.45  -i-  1.03  =  44.12  grs.  wt.  before  twisting. 

Draft  of  spinning  frame  10.05.    Double  2. 

44.12X10.05 

—  =  221.7  grs.  wt.  120  yds.  fine  roving. 

2 

221.7  -H  10  =  22.17  grs.  wt.  12  yds.  fine  roving  =  4.5  H.  R. 

Draft  of  fine  frame  5.74.    Double  2. 

22.17X5.74 

—  =  63.63     grs.     wt.     of     12     yards     of  intermediate  roving  = 


2  [1.57  or  1.6  H.  R. 

Draft  of  intermediate  4.79.  •  Double  2. 

63.63X4.79 


152.39  grs.  wt.  of  12  yds,  of  slubber  roving  =  .66  H.  R. 


Draft  of  slubber  3.83.     No  doublings. 

152.39X3.83 


=  48.6  or  49  grs.  wt.  of  1  yd.  sliver  on  back  of  slubber. 


12 

Draft  of  drawing  frame  6.    Double  6. 

This  does  not  change  the  weight  of  the  sliver,  hence  the 
•card  sliver  will  weigh  49  grs.  per  yard. 

Draft  of  card  100.    Allow  for  5%  waste. 

49X100 

—  =  11.2  oz.  lap  from  the  finisher  pickers. 
.95X437.5 

This  lap  is  too  light  and  could  easily  be  made  heavier,  by 
using  more  draft  on  the  fly  frames  and  spinning  frame,  thus  call- 
ing for  a  heavier  card  sliver. 

MACHINERY   EQUIPMENT. 

Having  worked  out  a  suitable  program  of  weights  and 
drafts,  the  next  step  is  to  estimate  the  production  required  at 
each  stage  of  the  operation.  In  getting  these  figures  we  must 
allow  a  certain  percentage  at  the  different  machines  for  waste 
and  stoppages.  It  would  be  impossible  to  produce  the  same  num- 


ORGANIZATION  SHEETS.  161 

ber  of  pounds  of  yarn  as  there  were  pounds  of  card  sliver,  as 
every  frame  the  material  passes  through  makes  some  waste,  due 
to  breakages,  etc.,  hence  it  is  imperative  to  start  with  more 
pounds  of  cotton  than  the  required  number  of  pounds  of  yarn. 
After  this  allowance  in  the  production  is  made  there  should  be  a 
certain  allowance  at  each  process  for  loss  of  time  while  doffing, 
oiling,  etc.  These  amounts  vary  with  different  machines  and 
also  with  the  same  machine  on  different  classes  of  work.  It 
is  not  possible  to  make  a  fixed  allowance  for  each  operation,  but 
a  fair  average  can  be  estimated  from  actual  results.  After  this 
average  allowance  has  been  provided  for  any  discrepancy  in  pro- 
duction can  be  easily  overcome  by  raising  or  lowering  the  speeds 
where  needed. 

It  is  not  the  best  policy  to  use  extra  large  machines  in  spin- 
ning and  roving  or  very  small  ones.  In  the  former  case  the  loss 
of  time  while  doffing,  etc.,  is  increased,  and  in  the  latter  the 
cost  of  production  is  increased.  It  is  not  well  to  use  excessive 
speeds  anywhere  as,  by  so  doing,  the  quality  of  the  product  is 
impaired  and  the  percentage  of  breakages  increased,  thus  in- 
creasing the  time  lost  and  the  percentage  of  waste  made. 

In  getting  the  figures  which  follow  it  has  been  endeavored 
to  strike  a  good  average  all  the  way  through,  without  excessive 
speeds  or  production,  which  will  give  a  good,  smooth,  strong  yarn 
at  the  spinning  with  the  minimum  of  stoppages  and  waste. 

SPINNING  SPINDLES. 

Speed  of  spindles  9,500  R.  P.  M.  Time  run  10  hours  per 
day.  Allow  for  10%  loss  of  time.  Product /on  constant,  under 
above  conditions,  is  169.65. 

V  22  X  4.75  =  22.28  turns  of  twist. 

169.65 

=  .34  Ibs.  per  spindle  per  day.         • 

22.28X22 

Total  spindles  in  the  mill  10,000,  then: 

10,000 X. 34  — 3,400  Ibs.of  yarn  per  day  produced  by  the  mill. 

Using  208  spindles  per  frame,  we  get : 

10,000  -*-  208  =  48  frames. 

This  figures  16  spindles  short  but  is  not  enough  to  be  con- 
sidered. 

FINE  FRAME. 

The  waste  between  the  fine  frame  and  yarn  wi'l  probably 
not  run  much  over  2%  and  the  time  allowed  for  stoppages,  for 


162  COTTON    MILL    MACHINERY    CALCULATIONS 

oiling,  doffing,  piecing-up,  etc.,  should  not  exceed  15%,  so,  in 
order  to  get  a  production  of  roving  sufficient  to  keep  the  spindles 
running,  we  must  make  these  two  allowances  and  figure,  in  one 
case,  for  a  2%  heavier  production  and,  in  the  other  case,  for  a 
15%  loss  of  time  on  the  frames. 

Spindle  production  3,400  Ibs. 

3,400  X  1.02  =  3,468  Ibs.  roving  required  from  fine  frames  to 
keep  spindles  running.  Speed  of  flyer  1,200  R.  P.  M.  Size  of 
bobbin  7  x  31/?  inches.  Hank  roving  4.5.  Twist  per  inch  in  the 
roving  is  V4.5  X  1.2  =  2.54  turns.  Loss  of  time  15%.  Diameter 
of  front  roll  IVs"-  Production  constant,  based  on  above  is  20.24. 

Then:       20.24 

=  1.77  Ibs.  per  spindle. 

2.54X4.5 

And     3,468  --  1.77  =  1,959  spindles. 

Allowing  160  spindles  to  a  frame,  we  get: 

1,959  -H 160  =  12  frames. 

This  figures  39  spindles  short  and  this  shortage  can  be  made 
up  by  getting  4  frames  of  168  spindles  each  instead  of  all  having 
160  spindles- 

INTERMEDIATE    FRAMES. 

Spindle  production  3,400.     Allow  4%  for  waste  of  material 
between  the  intermediate  roving  and  yarn,  then :  3,400  X  1-04  = 
3,536  Ibs.  of  roving  required  from  the  intermediate  spindles. 

Speed  of  flyer  950  R.  P.  M.  Size  of  bobbin  9  X  41/2  inches. 
Hank  roving  1.6.  Twist  in  the  roving  is  VI. 6  X  1.2  =  1.52  turns. 
Loss  of  time  18%.  Front  roll  li/4"  in  diameter.  Production  con- 
stant, based  on  above  conditions,  is  15.45. 

Then:     15.45 

—  =  6.35  Ibs.  per  spindle. 
1.52X1.6 

And:   3,536-^6.35  =  557    spindles. 

Allowing  96  spindles  to  a  frame,  we  get : 

557  -f-  96  =  6   frames. 

SLUBBERS. 

Spindle  production  3,400  Ibs.  Allow  8%  for  waste  of  ma- 
terial between  slubber  roving  and  yarn,  then :  3,400  X  1.08  = 
3,672  Ibs.  of  roving  required  from  the  slubbers.  ^ 

Speed  of  flyer  650  R.  P.  M.  Size  of  bobbin  12  x  6  inches. 
Hank  roving  .66.  Twist  per  inch  is  V. 66X1.2  =  .97  turns. 


ORGANIZATION  SHEETS.  163 

Front  roll  1J/4"  in  diameter.     Time  lost  20%.     Production  con- 
stant, based  on  above  conditions,  is  10.31. 

Then:     10.31 

=  16.11  Ibs.  per  spindle. 

.97X.66 

And:   3,672^-16.11  =  228   spindles. 

Allowing  56  spindles  to  a  frame,  we  get: 

228  -=-  56  =  4  frames. 

DRAWING. 

Spindle  production  3,400  Ibs.  Allow  10%  for  loss  of  material 
between  drawing  sliver  and  yarn,  then :  3.400  X  1.10  =  3,740  Ibs. 
sliver  required  from  the  draw  frames. 

Speed  of  front  roll  350  R.  P.  M.  1%"  metallic  front  roll, 
32  pitch.  Weight  of  sliver  49  grains.  Loss  of  time  20%.  Pro- 
duction constant,  under  above  conditions,  is  .01095. 

Then:    .01095X350X49  =  188  Ibs.  per  delivery. 
And:     3,672  -=-  188  =  19.5  or  20  deliveries. 

Using  4  deliveries  per  head  gives  one  drawing  frame  of  5 
heads  with  4  deliveries  each  for  each  process  of  drawing.  Use 
two  processes. 

CARDS. 

Spindle  production  3,400  Ibs.  Allow  12  per  cent,  for  loss  of 
material  between  card  sliver  and  yarn,  then : 

3,400  X  1.12  =  3,808    Ibs.    sliver  required   from   the   cards. 

Diameter  of  doffer  clothed  27.75".  Speed  of  doffer  14  R.  P.  M. 
Wt.  of  sliver  49  grs.  Time  lost  10%.  Production  constant,  based 
on  above  conditions,  is  .2111. 

Then:     .2111  X  14  X  49  =  145  Ibs.  per  card. 
And:       3,808  -f  145  =  26.2  or  26  cards. 

PICKERS. 

Spindle  production  3,400  Ibs.  Allow  20%  for  loss  of  material 
between  finished  laps  and  yarn,  then : 

3,400  X  1.20  =  4,080  Ibs.  of  lap  required  from  the  finishers. 

Speed  of  lap  rolls  7.75  R.  P.  M.  Diameter  of  lap  rolls  9". 
Weight  of  laps  11.2  ozs.  per  yd.  Time  lost  20%.  Production  con- 
stant, based  on  above  conditions,  is  23.56. 

Then:     23.56X7.75X11.2  =  2,038    Ibs.    per    picker. 
And:       4,080-^-2,038  =  2   finisher  pickers. 


164  COTTON    MILL    MACHINERY    CALCULATIONS 

This  will  call  for  2  intermediate  pickers  and  one  breaker  and 
one  opener  picker,  the  last  two  to  be  connected  by  dust  trunk  or 
other  suitable  connection. 

In  the  above  figures,  the  allowance  made  for  loss  of  mate- 
rial at  the  different  processes,  includes  the  waste  of  all  sorts,  a 
good  deal  of  which,  of  course,  is  perfectly  clean  and  can  be  used 
over. 

In  attempting  to  run  the  foregoing  program  with  the 
equipment  worked  out,  there  will,  in  all  probability,  be  some 
discrepancies  that  will  cause  a  little  trouble,  but  none  that  cannot 
be  overcome  by  readjusting  some  of  the  speeds,  etc.  There  should 
be  a  certain  amount  of  elasticity  in  every  program,  as  the  loss 
of  time  varies  with  the  efficiency  of  the  operatives  and  the  qual- 
ity of  work  done,  as  well  as  the  speed  used ;  the  production  like- 
wise varies  from  the  same  causes.  Reducing  the  speed  of  fly 
frames  will  often  increase  the  production  from  the  fact  that 
there  will  be  a  less  amount  of  lost  time  due  to  breakage  of  the 
roving,  etc. 

In  many  cases  higher  and  lower  speeds  than  those  given  are 
used  with  good  results,  greater  and  less  productions  obtained, 
more  and  less  time  lost  by  stoppages,  etc.,  but  the  allowances 
made  and  the  results  obtained  as  given  here  are  such  as  can  be 
equalled  and  in  many  cases  exceeded,  by  any  well-organized  and 
well-managed  mill. 

LOOM  EQUIPMENT. 

In  our  previous  figuring  we  have  not  taken  into  considera- 
tion any  calculations  for  determining  the  production  or  number 
of  looms,  the  figures  given  being  intended  for  a  mill  making 
yarns  for  the  market.  When  figuring  a  program  for  a  weaving 
mill,  the  number  of  looms  to  install  and  the  size  to  spin  our  warp 
and  filling  must  be  settled.  It  is  first  necessary  to  decide  upon 
the  style  of  goods  to  be  made,  that  is,  the  weight  per  yard,  the 
width  and  the  number  of  threads  of  warp  and  filling  to  use. 

Suppose  it  is  desired  to  build  a  mill  to  produce  plain  cloth, 
40  inches  wide,  68  threads  of  warp  and  filling  each  per  inch  and 
to  weight  4  yards  per  pound.  This  would  be  expressed  as,  68  x  68, 
40  inches,  4  yard  goods.  The  looms  are  to  run  160  picks  per  min- 
ute and  allow  for  15  per  cent,  loss  of  time.  The  mill  is  to  contain 
20,000  spindles. 

We  must  first  determine  the  sizes  of  warp  and  filling  yarns 
to  spin  to  make  a  cloth  of  the  above  construction.  To  do  this  we 
must  figure  the  average  number  of  yarn  in  the  cloth  and  from  this 
we  can  decide  upon  the  size  warp  yarn  to  use  and  figure  the  cor- 
responding size  of  filling  yarn.  On  the  above  class  of  goods  we 


ORGANIZATION  SHEETS.  165 

can  figure  the  warp  and  filling  to  take-up  about  8  per  cent,  in 
weaving  and  the  increase  in  weight  of  warp,  due  to  sizing,  as  6 
per  cent. 

Then :  68  x  40  =  2,720  ends  in  the  warp,  and,  2,720  +  24  = 
2,744  ends  in  the  warp  including  24  extra  ends  for  selvedges. 

As  the  warp  contracts  8  per  cent,  in  weaving,  it  will  take 
108  yards  of  warp  to  weave  100  yards  of  cloth,  then :  2,744  x 
108  =  296,352  yards  of  yarn  in  100  yards  of  cloth.  We  can  fig- 
ure the  increase  in  the  weight  of  warp  yarn,  due  to  the  added  size, 
as  an  increase  in  the  number  of  yards  and  get  correct  results, 
then :  296,352  X  1.06  =  314,133.12  yards  of  warp  yarn  allowing 
for  take-up  in  weaving  and  sizing.  And:  314,133.12 -=- 840 
=  373.76  hanks  of  warp  yarn  in  100  yards  of  cloth. 

The  width  in  the  loom  will  be  found  as  follows: 

40  -*•  .92  =  43.47  inches. 

Then:   43.47X68X106 

—  =  351.9    hanks    of   filling   in    100   yards    of   cloth. 

840 

And :  373.76  +  351.9  =  725.66  total  hanks  of  yarn  in  100 
yards  of  cloth.  The  cloth  weighs  4  yards  per  pound  and  100  yards 
will  weigh  25  pounds,  hence: 

725.66  -f-  25  ==  29.02  or  29's  counts  of  warp  and  filling  yarn  to  spin. 

As  it  is  customary  to  spin  the  warp  3  to  8  numbers  coarser 
than  the  filling,  we  will  assume  that  the  warp  is  to  be  spun  27's 
counts  and  work  out  the  required  size  of  filling.  We  found  that 
there  would  be  373.76  hanks  of  warp  yarn  in  100  yards  of  cloth, 
therefore :  373.76  -=-  27  =  13.84  pounds  as  the  weight  of  the  warp 
yarn,  and:  25  —  13.84  =  11.16  pounds  as  the  weight  of  the  filling 
yarn.  As  there  are  351.9  hanks  of  filling  yarn  in  100  yards  of 
cloth,  then:  851.9-4-11.16  =  31.63  or  practically  31.5's  counts 
of  filling  yarn  required. 

We  have  figured  the  warp,  in  100  yards  of  cloth,  to  weigh 
13.84  pounds  and  the  filling  11.16  pounds  which  gives  55.3  per 
cent,  warp  and  44.7  per  cent,  filling.  Then,  for  every  100  pounds 
of  yarn  spun  there  would  be  55.3  pounds  of  warp  and  44.7  pounds 
of  filling  and  the  total  spindles  in  the  mill  will  have  to  be  divided 
between  warp  and  filling  so  as  to  spin  the  yarns  according  to  the 
above  proportion. 

SPINDLES. 

Assume  the  warp  spindles  to  have  a  speed  of  9,500  R.  P.  M. 
and  allow  for  10  per  cent,  loss  of  time.  Production  constant,  for 
above  conditions,  is  165.  The  twist  is  24.68  turns  per  inch. 

Rule  for  using  production  constant: 


166  COTTON    MILL    MACHINERY    CALCULATIONS 

Constant  divided  by  the  counts  of  the  yarn  multiplied  by  the 
twist  per  inch  equals  the  pounds  per  spindle  per  day  of  10  hours 

Then:     165  -e-  27  X  24.68  =  .247  pounds  per  spindle  per  day. 
Therefore:     55.3  H-  .247  =  224  warp  spindles. 

Assume  the  filling  spindles  to  have  a  speed  of  8,300  R.  P.  M. 
and  allow  for  10  per  cent,  loss  of  time.  Production  constant,  for 
above  conditions,  is  147.  Then:  147  -=-  31.5  x  18.24  =  .255 
pounds  per  spindle  per  day.  Therefore :  44.7  -f-  .255  =  175  filling 
spindles.  This  gives  a  total  of  399  spindles  to  produce  the  above 
amount  of  warp  and  filling  yarns  in  the  proportion  needed  for  the 
cloth,  56  per  cent,  being  warp  spindles  and  44  per  cent,  being  fill- 
ing spindles  and  the  total  20,000  spindles  contained  in  the  mill 
must  be  divided  according  to  the  above  percentages.  This  gives 
11,200  warp  spindles  and  8,800  filling  spindles.  The  above  divided 
into  frames  of  208  spindles  each  will  give  54  warp  frames  and 
42  filling  frames. 

The  production  of  a  warp  spindle  was  found  to  be  .247 
pounds  per  day,  then :  11,200  X  .247  =  2,766  pounds  of  warp  yarn 
produced  per  day.  The  production  of  a  filling  spindle  was  found 
to  be  .255  pounds  per  day,  then :  8,880  x  .255  ==  2,244  pounds  of 
filling  yarn  produced  per  day.  Then  the  total  amount  of  yarn 
produced  will  be :  2,766  +  2,244  =  5,010  pounds  per  day.  Allow- 
ing for  an  average  loss  of  2  per  cent,  in  weaving  the  above  yarn 
into  cloth,  there  would  be  only  4,909  pounds  of  cloth  produced 
per  day. 

LOOMS. 

The  following  rule  will  give  the  production  per  loom  per  day 
in  pounds: 

Multiply  the  picks  per  minute  by  the  minutes  per  day,  with 
the  allowance  for  loss  of  time,  and  divide  this  by  the  product  of 
the  picks  per  inch  multiplied  by  36  and  by  the  yards  in  one  pound 
of  cloth. 

The  loom  speed  was  given  as  160  picks  per  minute  and  the 
loss  of  time  as  15  per  cent.,  then  the  following  will  give  the  pro- 
duction per  day: 

160X600X.85 

—  =  8.33  pounds  per  loom. 
68X36X4 

The  figures  above  gave  a  production  of  4,909  pounds  of 
cloth  per  day,  then :  4,909  -5-  8.33  =  558  looms. 

Assuming  any  given  number  of  looms  and  figuring  the  num- 
ber of  spindles  required  for  them  is  a  more  direct  method,  but 


ORGANIZATION   SHEETS.  167 

gives  no  very  definite  idea  of  the  number  of  spindles  required 
until  the  work  is  completed.  Where  it  is  desired  to  have  a  given 
number  of  spindles,  the  above  method  will  give  correct  results. 

In  installing  the  above  spinning  frames,  it  is  advisable  to  or- 
der several  frames  fitted  with  combination  builders  so  as  to  be 
able  to  spin  either  warp  or  filling  on  them.  In  this  way  the  pro- 
cess is  more  elastic  and  permits  the  spinning  of  more  or  less  warp 
or  filling  as  the  requirements  of  the  case  might  call  for. 


COTTON 
MACHINERY 


FEEDERS 

SELF-FEEDING    OPENERS 
BREAKER,    INTERMEDIATE    AND    FINISHER    LAPPERS 

REVOLVING    FLAT    CARDS 

DRAWING    FRAMES  (ELECTRIC  OR  MECHANICAL  STOP  MOTION) 
SLUBBING,     INTERMEDIATE.     ROVING     AND     JACK     FRAMES 

IMPROVED    SPINNING    FRAMES 
TWISTERS    FOR    WET    OR     DRY    WORK 

H,  &  B,  AMERICAN  MACHINE  COMPANY 

PAWTUCKET,  R,  I. 


BOSTON  OFFICE 

65  Franklin  St. 
C.  E.  RILEY,  Pres 


ATLANTA  OFFICE 

814  Empire  Bldg. 

E.CHAPPELL.SO.  Rep. 


COTTON   MILL    MACHINERY 
SPECIALISTS 


POTTER  &  JOHNSTON  MACHINE  CO. 

PAWTUCKET,  R.  I. 
Picking  Machinery  and  Revolving  Flat  Cards 

WOONSOCKET  MACHINE  &  PRESS  CO. 

WOONSOCKET,  R.  I. 
Drawing  Frames  and  Roving  Machinery 

FALES  &  JENKS  MACHINE  CO. 

PAWTUCKET,  R.  I. 
Spinning  and  Twisting  Frames 

EASTON  &  BURNHAM  MACHINE  CO. 

PAWTUCKET,  R.  I. 
Spooling  and  Winding  Machinery 

T.  C.  ENTWISTLE  CO. 

LOWELL,  MASS. 
,  Warping,  Beaming  and  Balling  Machinery 


SOUTHERN  AGENT 

J.  H.  Mayes,     -  Charlotte,  N.  C. 

1112  Independence  Building 


THE 

Whitin  Machine  Works 

WHITINSVILLE,  MASS. 

BUILDERS  OF 

COTTON  MILL 
MACHINERY 


Cards,  Combers,  Drawing  Frames, 

Roving  Frames, 

Spinning  Frames,  Spoolers, 

Twisters,  Reels, 

Long  Chain  Quillers,  Looms  and 
Dobbies 


SOUTHERN  AGENT 

STUART  W.  CRAMER 

CHARLOTTE,  N.  C. 


For  the  best  results  on  your  spinning  frames,  they 
should  be  equipped  with  our 

Rabbeth  Centrifugal  Clutch 
Spindles 

Mirror  Spinning  Rings 

(Trade  Mark  Reg.  U.  S.  Patent  Office) 

Rhoades-Chandler  Separators 

Shaw   &   Flynn    Lifting   Rod 
Clearers 

AND 

Speakman  Lever  Screws 


DRAPER  COMPANY 

HOPEDALE,  MASS. 

J.   D.  GLOUDMAN,   Southern  Agent, 
40  So.  Forsyth  St.,  Atlanta,  Ga. 


•  NORTHROP  LOOMS 


TRADE  MARK  REGISTERED 


for  fe Weaver 

Larger  Dividends  for  the  Mill 


DRAPER  COMPANY 

HOPEDALE,  MASS. 


t*4tHN+**4***HH**t>*l*l*+l**>«M>^^ 

SACO-LOWELL  SHOPS 

NEWTON  UPPER  FALLS  -LOWELL  -BIDDEFORD 

COMPLETE  COTTON  MILL 
EQUIPMENTS 

J    CARDS  DRAWING 

SLUBBERS  INTERMEDIATES 

FINE  FRAMES  JACK  FRAMES 

SPINNING  FRAMES  TWISTERS 

SPOOLERS  WARPERS         SLASHERS 

WARPER  BEAMS  SIZE  KETTLES 

SIZE  PUMPS  SIZE  SYSTEMS 

BALLERS  DUCK  BEAMERS 

PLAIN    FANCY    AND    DUCK    LOOMS 
CAMLESS  WINDERS 


SOUTHERN  OFFICE: 

CHARLOTTE,  N.  C 

ROGERS  W.  DAVIS,  SOUTHERN  AGENT 


SAGO-LOWELL  SHOPS 

«& 

NEWTON  UPPER  FALLS— LOWELL-  BIDDEFORD 

MANUFACTURERS  OF  COMPLETE 

PICKING  AND  WASTE  RECLAIMING 
EQUIPMENTS 

Bale  Breakers        Conveying  Systems 
Condensers  Distributors 

Breaker  Lappers    Intermediates 

Finisher  Lappers    Thread  Extractors 
Roving  Waste  Openers 

Hard  Waste  Openers 
Card  and  Picker  Waste  Cleaners 
|  4-Coiler  Waste  Cards          Lap  Winders 

SOUTHERN  OFFICE: 

CHARLOTTE,  N.  C. 

ROGERS  W,  DAVIS,  SOUTHERN  AGENT 


COTTON  MILL  MACHINERY 

CARDS  SPINNING 

MASON 
MACHINE  WORKS 

TAUNTON,  MASS. 

MULES  LOOMS 


Southern  Office,  Charlotte,  N,  C,     EDWIN  HOWARD,  Agent 

H»$MH$«H|H»*»««4H«HiM*«^H»4h**H^^  ^ 

Win.  Firth,  Pres.          Edwin  Barnes,  Vice-Pres.         John  H.  Nelson,  Treas- 

WILLIAM  FIRTH  COMPANY     ! 

558-559  John  Hancock  Bldg.,  200  Devonshire  St.,  Boston,  Mass. 
Sole  Importers  of 

ASA  LEES  &  COMPANY,  LIMITED 

TEXTILE  MACHINERY 
of   every  description   for    cotton,    woolen    and    worsted 

SOLE  AGENTS  FOR 
Joseph  Stubbs,  Limited,  Gassing,  Winding  and  Reeling  Machinery  for  Cotton,  Worsted 

and  Silk. 

George  Orme  &  Co  ,  Patent  Hank  Indicators,  Etc. 
William  Tatham,  Limited,  Waste  Machinery 
R.  Centner  Fils,  Heddles. 

Goodbrand  &  Co.,  Yarn  Testing  Machinery,  Warp  Reels,  Etc. 
Joshua  Kershaw  &  Son,  English  Roller  Skins,  Etc. 
Buckley  &  Crossley,  Spindles,  Flyers  and  Pressers,  Etc. 
George  Smith,  Doffer  Combs.  Etc. 
Bradford  Steel  Pin  Co.,  Comber  Pins. 

ALSO  AGENTS  FOR 

Joseph  Sykes  Bros.,  Hardened  and  tempered  steel  Card  Clothing  for  Cotton. 
Dronsfield  Bros.,  Limited,  Emery  Wheel  Grinders,  Emery  Fillet  and  Flat  Grinding 

Machines. 

United  Velvet  Cutters  Association,  Limited,  Corduroy  Cutting  Machines,  Etc. 
George  Thomas  &  Co..  Tachometers,  &e. 

Pick  Glasses,  Leather  Aprons,  Patent  Wire  Chain  Aprons. 


CALL  ON   US 
WHEN   YOU   COME  TO  TOWN 


MODERN    POWER   PLANTS  STEAM  HYDRAULIC  ELECTRIC 

A.    H.    WASHBURN    CO. 

CONTRACTING     ENGINEERS 
CHARLOTTE,   N.  C.  REALTY   BLDG. 


SOUTHERN    AGENTS 

CURTIS     &     MARBLE     MACHINE    CO. 


YOU    WILL   BE 
CORDIALLY   RECEIVED 


PICKING  MACHINERY 
REVOLVING  FLAT  CARDS 

LAP  WINDERS 

DRAWING  FRAMES  . 

EVENER  DRAWING 

FRAMES 


WE  WANT  YOU  TO 
LEARN  ABOUT  THE 
MANY  IMPROVE- 
MENTS WE  HAVE 
MADE 


SAGO-LOWELL 
SHOPS 

BUILDERS  OF 

IMPROVED 
COTTON 

MILL 
MACHINERY 


SLUBBERS 
INTERMEDIATES  FINE 

and 
JACK  ROVING  FRAMES 

SPINNING  FRAMES 
SPOOLERS  and  REELS 


WORKS  AT 


NEWTON  UPPER  FALLS,  MASS, 

BIDDEFORD,  MAINE 

LOWELL,  MASS. 


WE  WANT  EVERY- 
BODY TO  KNOW 
HOW  WELL  WE 
BUILD  OUR 
MACHINERY 


ROGERS  W.  DAVIS 

SOUTHERN  AGENT 

Suite  1000  Realty  Building 

CHARLOTTE,  N.  C. 


Manufacturers  should  look  up  the  advantages  of    *  * 

The  Metallic 
Drawing  Roll 

f  •^— ^— — — — ^— • 

f    Over  the  leather  system  before  placing  orders  for 
f    new  machinery,  or,  if  contemplating  an  increase 

fin  production,   have  them  applied  to  their    old 
machinery. 


25  TO  33  PER  CENT 
More  Production  Guaranteed 


Saves :  Roll  Covering,  Varnishing,  Floor  Space,  Power,     T 
Waste  and  Wear. 

One-Third  Less  Weight  Required 

Runs  Successfully  on  :  Railway  Heads,  Drawing  Frames, 
Sliver  Laps,    Ribbon    Laps,    Comber   Draw    Boxes,     «> 
Detaching  Rolls,   Slubbers  and  Intermediate  Roving 
Frames. 


Write  for  points  claimed  and  particulars  to 

THE  METALLIC  DRAWING  ROLL  CO. 

Indian  Orchard,  Massachusetts 


{  TheHigbest  Standard  of 
Loom  Harness  Quality 


Those  who  use  our  loom  harnesses 
little  realize  how  many  harnesses 
fail  to  pass  the  rigid  inspection 
which  they  are  obliged  to  undergo. 
We  criticize  our  own  work  more 
severely  than  it  is  criticized  by 
anyone  else  and  throw  out  harnesses 
which  probably  would  not  be  criti- 
cized by  the  user.  It  is  this 
policy  which  has  given  our  harnesses 
a  reputation  for  always  being  uni- 
form in  quality. 


Let  us  tell  you  more  about  these  Harnesses. 
GARLAND  MFG.   CO.,   Saco,  Maine 


This   Spinning  Frame 

was  originally  built  wiih  ordinary  plain  bearings  on  the  two  laige  vertical 
shafts.  y£  horsepower  was  required  to  run  it,  and  the  plain  bearings  heated 
so  that  the  machine  had  to  be  stopped  after  a  half-hour's  run. 

HESS  -BRIGHT  BALL  BEARINGC 
JBvii.lt     for     E^ncJiJLT'a.nc.e/         VJ 


The  Hess- 

r   %-^.- 


were  substituted   for  the  plain  bearings.     The   power  required   was  thereby 
reduced  to  2%  horsepower,  and  the  machine  runs  all  day  without  heating. 
The  Hess-Brights  require  oiling  only  about  once  in  six  months,  and  no  other 
attention  of  any  sort.     They  are  permanently 
snug,  as  well  as  cool  and  free-running. 

Hess-Brights  are  solving  difficult  bearing 
problems  for  many  builders  and  users  of 
textile  machinery. 

Hess  Bright  Ball  Bearing  Line  Shaft 
Hangers  are  the  most  frictionless  and  most 
durable  of  their  kind.  The  highest  in  price, 
they  are  the  most  economical  in  the  end. 

Our  Engineering  Department  will  answer 
your  request  for  further  information. 

THE  HESS-BRIGHT  MFG.  COMPANY 

55  East  Erie  A  >•••..  Philadelphia.  Pa. 


ar^Jp.^      :nj.p^*y 


THE  STANDARD  SINGE  1835 

HOYT'S  FLINT  STONE  LEATHER  BELTING 


THE  best  drawn  and  most  exacting  belt  specifications  f 
will  not  insure  your  getting  the  best  belt  for  your 

service. 

Your  machinery  might  require  an  extra  heavy  single  f 

belt, — or  on  the  other  hand  a  light  double  thick  one  would  4 

more  favorably  influence  toward    the  highest  machine  * 

efficiency.  4 

Hoyt's  Flintstone  Leather  Belting  is  cut  and  built  4 

with  a  view  to  its  meeting  the  most  exacting  require-  ^ 
ments  of  shop  and  machine  tool  operation. 

Two  different  Hoyt's  Flintstone  Belts,  designed  to  T 

meet  the  same  conditions  will  gauge  up  to  within  almost  T 

micrometer  measurement  of  each  other.  f 

We  have  employes  who  have-  been  with  us  for  over  f 

forty  years  (and  younger  ones  following  in  their  foot-  4* 

steps)   who  have  never  worked  elsewhere.     These  men  <{, 

will  gauge  a  hide  to  make  a  certain  weight  belt^  and  when  & 

the  belt  is  built  an  accurate  scale  will  show  their  selection  T 

to  have  been  as  nearly  correct  as  predetermination  can  t 

make.  £ 

That  is  but  one  feature  of  the  expert  service  that  1 
helps  to  make  Flintstone  Leather  Belting  the  best  that's 
made' 

Let  our  corps  of  belting  engineers  sugg'est  the  solu- 
tion  of  your  problems. 


ESTATE 

Edward   R.   Ladew 

GLEN  COVE,  N.  Y. 

Charlotte,  N.  C.  New  York.  Boston  Pittsburg 

Philadelphia  Newaik,  N.  J.  Chicago  Tacoma 

Portland,  Ore.  Providence,  R.  I.  Atlanta  Milwaukee 


EMMONS  LOOM 
HARNESS  CO. 

MAY  STREET,  LAWRENCE,  MASS. 


COTTON  HARNESS,  MAN.  HARNESS  AND  REEDS 

For  Cotton,  Duck,  Worsted  and  Silk  Goods 

SELVEDGE  HARNESS 

Any  depth  up  to  24  inches,  for  weaving  Tape  Selvedges 

Beamer  anil  Dresser  Hecks  Mending  Eyes  and  Mending  Twine 

Slasher  and  Striking  Combs  Warper  and  Leice  Reeds 


Baked  HS 


I  English  .Harness  Mail  Jacqnard  Meddles 

1  »._-,  "arness  Cotton  Selvedges 

Braided  Heddles      Mail  Selvedges 

4> 

1  For  Broad  Silks  and  Ribbons  • 

f    "  Emmons'  False    Reed  "  or  Thread  Clearer 

L 

T  .  Patented  Feb.  13,  1906 

If  A    CLEARER    MADE    OFTHREAD,    BAKED    FINISH 

Will  wear  as  long  as  the  harness 


ALFRED  SUTER 

2OO  FIFTH  AVENUE,  NEW  YORK 


TEXTILE 
ENGINEER 


Importer  of  Baer's  Yarn  and 
Cloth  Testing  Apparatus 

,  such  as 

Direct  Yarn  Numbering  Scales 
Yarn  and  Roving  Reels 
Twist  Testers 
Strength  Testers 
Conditioning  Ovens 
Evenness  Testers 
Microscopes 
Pick  Counters 
Hank   Counters  for   Spinning 

Frames,  etc.* 

also 

Warp  Sizing  Machines 
Yarn  Conditioning  Apparatus 
Yarn   and   Cloth   Mercerizing 
Machines  of  Latest  Types 

CATALOGUES    AND    INFORMATION 


I  BERLIN  ANILINE  WORKS 

t 

Main  Office:  213-215  Water  Street,  New  York 
Branches:  Boston;  Chicago;  Philadelphia;  Montreal 

SOUTHERN  BRANCH 

TRUST  BUILDING,  CHARLOTTE,  N.  C  * 


Dyes    for    All    Textile    Purposes 

Direct  Colors,  Sulphur  Colors,  Developed 
Colors,   Aniline    Salt,    Aniline    Oil,  etc. 

Constantly   bringing    out   New   and   Improved    Products 

Capable  Salesmen  and  Expert  Demonstrators 
connected  with  all  offices 

4    The    Most    Popular    Dye    Concern    in    the    World    < 


Economical  Cotton 

Dyeing  and  Bleaching 

In  the  Psarski  Dyeing  Machine 


Saves  Labor 
Saves  Dyes 
Saves  Drugs 

Saves  Steam 
Saves  Water 


Saves 
Fibre 


Sulphur — Developed — Vat  Dyes 

Done  Equally  Well 


balls  and  strings. 


BLEACHING  _  Bleached  and  washed  PERFECTLY  CLEAN—  FREE  FROM  CHLORIN  OR  ACID. 

^-^T.^a^yj  .  batch      u  no(  pounded  and  twisted  into 


SKEIN  DYEING—  No  BoiUn*  Out-No  Tangles-Yarn.  are  left  Smooth  and  in  perfect  condition  for 
—————        winding,  knitting,  etc. 

HOSIERY  _  Recommended  size  of  machine  does  300  pounds  to  batch,  SULPHUR  OR  DEVELOPED 
BLACKS.     It  is  not  Roughed-No  Singeing  required-No  Sorting-No  Damaged. 

15  to  20  per  cent  Saving  in  Drugs 

The  Psarski  Dyeing  Machine  Co. 

3167  Fulton  Road  CLEVELAND,  OHIO 


F.  J.  MUIR 

Agent  Southern'  State. 


WM.  1NMAN 

964  No.  Cambridge  St.,  Milwaukee 
Agent  Western  State. 


R.  D.  BOOTH 

933  No.  Broad  St.,  Philadelphia 
Agent  Eastern  State. 


Problems  in  Dyeing 

E  are  prepared  to  dye  any  shade  upon 
any    fabric     submitted,    or    we    will 
match  any  required  shade  and   sub- 
mit exact  dyeing  directions.     Infor-  <t 
I                 mation    of    a    technical    nature    cheerfully 

given.     No  charge  is  made  for  such  service,  T 

and  in  accepting  it  there  is  no  obligation  to 
purchase  from    us    anything    that  you    can  T 

f  buy  or  that  you  think  you  can  buy  to  better   ' 

*  advantage  elsewhere. 

I  Gassella  Color  Company 

182-184  Front  Street  :    New  York 

t      BOSTON,  39  Oliver  Street  PHILADELPHIA    126-1 28  S.  Front  St. 

*  PROVIDENCE,  64  Exchange  Place  ATLANTA,  47  N.  Pryor  St. 

MONTREAL,  59  William  Street, 


I"|E  HAVEN'S  High  Carbon  Steel  Spinning  Travelers, 
-*^  Bronze  Composition  and  Bronze  Twister  Travelers. 
Specially  treated  Travelers  for  silk  spinning. 

DE  HAVEN'S  High  Carbon  Steel  Spinning  Traveler 
is  the  only  Traveler  on  the  market  made  from  steel  wire  in 
which  the  hardening  elements  are  introduced  before  the 
Travelers  are  formed.  They  are  the  most  uniform  in 
temper,  and  the  most  durable  Travelers  manufactured- 

MADE  ONLY  BY 

De  Haven  Manufacturing  Go. 

50  Columbia  Heights  BROOKLYN,  N.   Y. 

BRANCHES 
Chicago,  San  Francisco,  Glasgow  and  London 


IT    PAYS    TO    USE    THE    BEST 
SHUTTLE  POSSIBLE  TO  OBTAIN 

THE  GAIN  IN  EFFICIENCY 
OF  YOUR  LOOMS  AND  THE 
LESSENED  YEARLY  COST  -FOR 
SHUTTLES  WARRANT  USING 

SHAMBOW   SHUTTLES 


WILLIAM  FIRTH.  Pres,  FRANK  B.  COMINS,  Vice-Pres.  and  Treas. 

AMERICAN  MOISTENING  COMPANY   I 

J20  Franklin  Street,  Boston,  Mass. 

Comins  Sectional   Humidifier  | 

Makes  This  System  Absolutely  Perfect  | 

Our  system  has  been  most  advantageously  adopted  by  the  representative  mills  of       J, 
this  country.    Our  system  will  increase  your  production  and  overcome  troublesome 
electricity,  making  your  carding,  spinning  and  weaving  run  much  better.    It  will  reduce 
your    waste  account  and  generally  prove  a  profitable  investment.    With  our  system  a 

•      PERFECT  CARDING.  SPINNING  OR  WEAVING  ATMOSPHFRE 
IN  ANY  CLIMATE  OR  WEATHER  IS  ASSURED 

Over   70.000  of   our   Humidifiers  in  Operation 

Purifies  the  Air  and  makes  it  Healthier  for  the  Workpeople 
Write  for  Booklet  on  Humidification 

Southern   Representative:     JOHN  HILL 

Atlanta.,  Ga. 


WOONSOCKET,  R.  I. 


What 

4c  a  Month 

Will  Do  for  You 


You  buy  your  magazines  for  their 
value  to  you  and  irrespective  of 
their  price.  You  are  not  adverse 
to  getting  big  value  at  small  cost. 
Here  it  is. 

COTTON  will  bring  you  the 
best  ideas  of  a  long  line  of  able 
and  practical  men.  These  men 
are  paid  contributors.  You  could 
not  buy  their  individual  service  and 
advice  short  of  many  hundreds  of 
dollars. 

For  $1  you  can  get  COTTON 
two  years.  It  will  contain  over 
800  pages  of  reading  matter  per- 
taining to  textile  work.  Almost  an 
encyclopedia  of  textile  information. 

Sample  copy  free  on  request. 


COTTON  PUBLISHING  GO. 

Atlanta,  Ga. 


"The  Blue  Book/'  Textile  Directory 


The  only 
Textile 
Directory 
issued  with 


thumb 
indexes 

for    quirk 

reference. 


Contains  the  Latest  Reports  from  all 


Cotton  Mills 

Woolen  and  Worsted  Mills 

Carpet  Mills 

Silk  Mills 

Knitting  Mills 

Jute,  Linen  and  Flax  Mills 

Canadian  Mills 

Dyers,  Finishers  and  Bleachers 

Dry  Goods  Commission  Merchants 


Cotton  Goods  Converters 

Yarn  Dealers  J. 

Raw  Silk  Importers,  Dealers,  Etc. 

Cotton  Dealers 

Mattress  Manufacturers 

Wool  and  Hair  Dealers 

Waste  Dealers  and  Manufacturers      *  ' 

Wholesale  Rag  Dealers 

Fibre  Brokers 


Separate  List  of  New  Mills 

Textile  Maps  of  the  New  England  States.   Middle  Atlantic  States.   Middle  Western 

States  and  Southern  States,  showing  all  Towns  at  which  Mills  are  located 
List  of  572  Railroads  on  which.Textile  Mill  Towns  are  located 

Thumb  Index  dividing  Office  Edition  into  14  Sections,  Pocket  Edition  into  12  Sections 
Alphabetical  Index  to  Mills  and  Owners 
Classified  Directory  of  Cotton  and  Woolen  Mills,  showing  under  each  heading  all  Mills 

making  each  line  of  goods,  with  Nos.  of  Yarns  made  by  Spinners 
Textile  Supply  Directory,  giving  Manufacturers  of  Chemicals,   Dye  Stuffs,    Yarns 

Textile  Machinery  and  Supplies  of  all  kinds,  this  enabling  the  trade  to  communicate 

with  first  hands. 

A  SPECIMEN  MILL  REPORT 

SOUTH  CAROLINA. 

LANCASTER,  Lancaster  Co.     (N.)    Pop.  3.500.    RR.  250.443. 

Lancaster  Cotton  Mills.  Inc.  1905.  Cap.  $1,000,000.  Leroy  Springs,  Pres.;  W.  C. 
Thomson,  Sec. ,  Treas,  and  Buyer;  A.  H.  Robbins,  Supt.  Sheetings  and  1  to  30 
Single  and  Ply  Yarns  for  market.  120  Cards.  1,578  Broad  Looms  74,184  Ring 
Spindles.  11  Boilers.  Electric  Power.  Employ  1,050-  Deering,  Milliken  &  Co., 
N.  Y.  and  Boston  Selling  Agts.  for  Cloth;  Yarns  sold  direct. 


Office  Edition,  1,100  Pages,  Price  $4,  Delivered.    Pocket  Edition,  1,000  Pages,  Price  $3,  Delivered      ? 

Circular  giving  full  contents  tent  on  request  T 

DAVISON    PUBLISHING    COMPANY,   407   Broadway,  New   York          f 


FIRE  :  LIGHTNING  :  WINDSTORM 

The  TJAM U  INSURANCE  COMPANY 

NEW  YORK 


1HOME 


ELBRIDGE  G.  SNOW,  President 
Organized  1853  Main  Offices  56  Cedar  St. 

CaLsh  Capital,  $3,000.000 

t  Assets,  January  1,  1912       ....  $32,146,565 

t  Liabilities  (Including  Capital)        .        .        .  16,521,125 

Y  Reserve  as  a  Conflagration  Surplus    .        .  1,800,000 

4  Net  Surplus  over  all  Liabilities  and  Reserves  13,815,440 

,t  Surplus  as  Regards  Policy  Holders     .        .  18,615,440 

|  Losses  Paid  Since  Organization,  over    .        .  132,000,000 

4*  Any  one  interested  in  maintaining  a  manufacturing  or  distributing  plant  may  have,       *  > 

for  the  asking,  helpful  suggestions  and  proper  advices  relating  to  the  Standards  of        • 
<f        CONSTRUCTION  and   PROTECTION   and  safeguarding  of  the  FIRE  HAZARD  by 
?         applying  to  the  agents  of  tfie  HOME  INSURANCE  COMPANY,  anywhere,  or  to  the 
Department  of  Improved  Risks,  56  Cedar  Street,  New  York  City. 


1  TEXTILE  DEPARTMENT 

NORTH  CAROLINA 

A.  and  M.  COLLEGE. 

FULL    EQUIPMENT    FOR    PRACTICAL    AND    THEORETICAL 
INSTRUCTION    IN   COTTON    MANUFACTURING. 

COURSE    OF     INSTRUCTION: 

1 .  Two  Year  Course  in  Cotton  Manufacturing. 

2.  Four  Year  Course  in  Cotton  Manufacturing. 

3.  Textile  Chemistry  and  Dyeing. 

The  courses  include  Picking;  Carding;   Combing;  Ring  and  Mule 
.       Spinning;  Warp  Preparation;  Designing;   Plain,  -Dobby  and  Jacquard     ' ' 
*      Weaving;  Textile  Chemistry  and  Dyeing;  Mill  Accounting. 

For  catalogue  and  other  information,  address, 

THOMAS  NELSON, 

WEST   RALEIGH,    N.  C. 


UNIVERSITY  OF  CALIFORNIA,  LOS  ANGELES 

THE  UNIVERSITY  LIBRARY 
This  book  is  DUE  on  the  last  date  stamped  below 


Form  L-9 
2cm-2,'43(520o) 


UNIVERSITY  of  CALIFORNIA 

AT 


1681  Park 


P22c  Cotton  mill  mach 
— inery  caloula- — - 
tions . 


TS 

1581 

P22c 


